KR102214281B1 - Refrigeration cycle and Refrigerator having the same - Google Patents

Abstract

In the refrigeration cycle of the present invention, the refrigerant discharged from the compressor flows to the compressor through a condenser, an ejector, a first evaporator, and a second evaporator, and a refrigerant in the first refrigerant circuit bypasses the first evaporator. A second refrigerant circuit configured to pass, and a third refrigerant branched at a branch point provided downstream of the condenser in the first refrigerant circuit or the second refrigerant circuit, so that the refrigerant joins the ejector through the expansion device and the third evaporator. A circuit, and the refrigerant is provided to flow through any one of the first refrigerant circuit and the second refrigerant circuit and the third refrigerant circuit. Through this configuration, COP can be improved, and cooling efficiency for a plurality of cooling chambers can be improved.

Description

Refrigeration cycle and refrigerator having the same {Refrigeration cycle and Refrigerator having the same}

The present invention relates to a refrigeration cycle and a refrigerator having the same, and more particularly, to a refrigeration cycle having an improved coefficient of performance (COP) and a refrigerator having the same.

In a cooling apparatus having two or more cooling chambers, each cooling chamber is partitioned by an intermediate partition wall and opened and closed by a door. In addition, an evaporator for generating cold air and a fan for blowing the generated cold air into the cooling chamber are provided for each cooling chamber. Since all cooling chambers are independently cooled by the action of each evaporator and fan, such a cooling method is called an independent cooling method. A typical cooling device to which the independent cooling method is applied is a refrigerator having a freezer compartment and a refrigerator compartment. The freezer of the refrigerator is mainly for storing frozen food, and the appropriate temperature of the freezer generally known is about -18℃. In contrast, the refrigerating chamber is known to be suitable for storing general foods that do not require freezing at room temperature of 0°C or higher.

Even though the appropriate temperatures of the refrigerating chamber and the freezing chamber are different from each other, in a conventional refrigerator, the evaporation temperatures of the first evaporator and the second evaporator are the same. For this reason, the freezing compartment fan is continuously operated, and the refrigerating compartment fan is operated intermittently to blow cold air into the refrigerating compartment whenever necessary so that the internal temperature of the refrigerating compartment is not lowered more than necessary.

An aspect of the present invention provides a refrigeration cycle having an improved coefficient of performance (COP) and a refrigerator having the same.

The refrigeration cycle according to the spirit of the present invention includes: a first refrigerant circuit configured to flow to the compressor through a condenser, an ejector, a first evaporator, and a second evaporator; A second refrigerant circuit configured such that the refrigerant bypasses the first evaporator in the first refrigerant circuit; A third refrigerant circuit branched at a branch point provided downstream of the condenser in the first refrigerant circuit or the second refrigerant circuit, and configured to join the refrigerant to the ejector via an expansion device and a third evaporator; and a refrigerant Is provided to flow through any one of the first refrigerant circuit and the second refrigerant circuit and the third refrigerant circuit.

It may be characterized in that the overall cooling mode in which the refrigerant flows through the first refrigerant circuit and the third refrigerant circuit and the refrigeration cooling mode in which the refrigerant flows through the second refrigerant circuit and the third refrigerant circuit are operated.

The expansion device includes a first expansion device and a second expansion device arranged in series with the first expansion device, wherein the third refrigerant circuit includes the first expansion device provided upstream of the third evaporator. A 3a refrigerant circuit provided to pass through; And a 3b refrigerant circuit provided to pass through the first expansion device and the second expansion device.

In the total cooling mode, at least a portion of the refrigerant flowing through the first refrigerant circuit circulates through the third a refrigerant circuit, and in the refrigeration cooling mode, at least a portion of the refrigerant flowing through the second refrigerant circuit is It may be characterized by circulating the 3b refrigerant circuit.

A first cooling chamber in which the first evaporator is disposed; And a second cooling chamber in which the second evaporator and the third evaporator are disposed, and formed at a lower temperature than the first cooling chamber.

A total cooling mode in which a refrigerant flows through the first refrigerant circuit and a third refrigerant circuit and a refrigerant cooling mode in which the refrigerant flows through the second refrigerant circuit and the third refrigerant circuit are operated, and in the total cooling mode operation, The first cooling chamber and the second cooling chamber may be cooled, and in the freezing cooling mode operation, the second cooling chamber may be cooled.

The second cooling chamber includes a blowing fan provided for air flow therein, and the third evaporator is disposed downstream of the second evaporator with respect to the air flow direction by the blowing fan. can do.

The refrigerant discharged from the condenser may include a main refrigerant introduced into the ejector through the first refrigerant circuit or the second refrigerant circuit; And a sub-refrigerant branching at the branch point and flowing through a third refrigerant circuit to merge with the main refrigerant in the ejector.

A first flow path switching device provided to allow the refrigerant discharged from the ejector to flow through at least one of the first refrigerant circuit and the second refrigerant circuit; And a second flow path switching device provided so that the refrigerant branching from the branch point to the third refrigerant circuit flows through any one of the 3a refrigerant circuit and the 3b refrigerant circuit. have.

The ejector may be characterized in that the refrigerant discharged from the condenser and the refrigerant discharged from the third evaporator are mixed and boosted and introduced into the compressor.

The ejector may include a nozzle part provided to expand the refrigerant discharged from the condenser under reduced pressure; A suction unit for sucking the refrigerant discharged from the third evaporator; A mixing unit in which the refrigerant introduced into the nozzle unit and the refrigerant introduced into the suction unit are mixed; And a diffuser unit provided to boost the refrigerant mixed in the mixing unit.

The nozzle unit includes a nozzle body, a nozzle inlet through which refrigerant flows into the nozzle body, and a nozzle discharge unit formed to have a width greater than that of the nozzle inlet through which the refrigerant is discharged from the nozzle body. The ejector may be characterized in that it comprises a; a needle portion formed in a cross-section that is variable with respect to the longitudinal direction, and provided to be able to advance and retract in the nozzle inlet.

And a first heat exchanger for exchanging heat between the first expansion device and the suction part of the compressor so that the refrigerant sucked into the compressor is overheated.

It may be characterized in that it further comprises a; a second heat exchanger for heat exchange between the suction portion of the compressor and the discharge portion of the condenser.

And a second heat exchanger for exchanging heat between the suction part of the compressor and a point downstream of the branch point in the first refrigerant circuit or the second refrigerant circuit.

And a first heat exchanger for exchanging heat between the first expansion device, the second expansion device, and the suction part of the compressor so that the refrigerant sucked into the compressor is overheated.

It may further include a second heat exchanger for heat exchange between the suction part of the compressor and the discharge part of the condenser.

And a second heat exchanger for exchanging heat between the suction part of the compressor and a point downstream of the branch point in the first refrigerant circuit or the second refrigerant circuit.

It may further include a third expansion device provided in the discharge portion of the condenser; a first heat exchanger for heat exchange between the third expansion device and the suction portion of the compressor; may further include.

The expansion device may include a capillary tube, an electronic expansion valve (EV), and a capillary tube.

The refrigeration cycle according to the spirit of the present invention includes a compressor; A condenser for condensing the refrigerant discharged from the compressor; An ejector through which a main refrigerant, which is at least a part of the refrigerant discharged from the condenser, flows in; A first evaporator provided in the first cooling chamber, and a second evaporator provided in a second cooling chamber having a lower temperature than the first cooling chamber, and the refrigerant discharged from the ejector flows in and heat exchange with the surroundings to the compressor. A main evaporator for discharging a refrigerant; An expansion device for moving the remaining sub-refrigerant among the refrigerants discharged from the condenser; A sub-evaporator provided in the second cooling chamber through which the sub-refrigerant passed through the expansion device flows so as to have a third evaporator provided in the second cooling chamber and heat exchange with the surrounding to send the sub-refrigerant to the ejector; And a first flow path switching device provided so that the refrigerant discharged from the ejector passes through at least one of the first evaporator and the second evaporator.

The expansion device includes a first expansion device and a second expansion device arranged in series with the first expansion device, and the refrigeration cycle is disposed upstream of the expansion device and passes through the first expansion device. Or, a second flow path switching device provided to pass through the first expansion device and the second expansion device; may be characterized in that it comprises a.

The first flow path switching device may be provided to selectively flow the refrigerant discharged from the ejector through the first evaporator and the second evaporator.

The ejector may be characterized in that the main refrigerant discharged from the condenser and the sub-refrigerant discharged from the sub-evaporator are mixed and boosted and introduced into the compressor.

The refrigerator according to the spirit of the present invention includes a main body; A first cooling chamber provided inside the main body, and a second cooling chamber formed at a lower temperature than the first cooling chamber; A refrigeration cycle for cooling the first cooling chamber and the second cooling chamber, wherein the refrigeration cycle includes a condenser, an ejector, a first evaporator in which the refrigerant discharged from the compressor communicates with the first cooling chamber, and the second cooling A first refrigerant circuit configured to flow to the compressor through a second evaporator in communication with the chamber; A second refrigerant circuit configured such that the refrigerant bypasses the first evaporator in the first refrigerant circuit; A third refrigerant circuit branched at a branch point provided downstream of the condenser in the first refrigerant circuit or the second refrigerant circuit, and configured to join the ejector through an expansion device and a third evaporator in communication with the second cooling chamber; It characterized in that it comprises a.

The refrigeration cycle may include an overall cooling mode in which refrigerant flows through the first refrigerant circuit and the third refrigerant circuit; And a refrigeration/cooling mode in which the refrigerant flows through the second refrigerant circuit and the third refrigerant circuit.

The expansion device includes a first expansion device and a second expansion device arranged in series with the first expansion device, wherein the third refrigerant circuit includes the first expansion device provided upstream of the third evaporator. A 3a refrigerant circuit provided to pass through; And a 3b refrigerant circuit provided to pass through the first expansion device and the second expansion device.

The ejector may be arranged in the direction of gravity than the third evaporator.

One aspect of the present invention can improve the COP (Coefficient of performance, performance coefficient) of the refrigeration cycle.

Also, energy efficiency can be improved by using an ejector.

In addition, since a plurality of cooling chambers can be separately cooled, cooling efficiency can be improved.

1 is a view of a refrigeration cycle according to a first embodiment of the present invention.
Figure 2 is a view of the flow of the refrigerant in the refrigeration cycle according to the first embodiment of the present invention.
3 is a view of the ejector of the refrigeration cycle according to the first embodiment of the present invention.
Figure 4 is a view of the operation of a partial configuration of the refrigeration cycle according to the operation mode according to the first embodiment of the present invention.
5 is a control diagram of a refrigeration cycle according to the first embodiment of the present invention.
6A and 6B are views illustrating an arrangement of a refrigerator and a refrigeration cycle according to the first embodiment of the present invention.
7 is a view of a refrigeration cycle according to a second embodiment of the present invention.
8 is a view of the flow of refrigerant in a refrigeration cycle according to a second embodiment of the present invention.
9 is a view of a refrigeration cycle according to a third embodiment of the present invention.
10 is a view of the flow of refrigerant in a refrigeration cycle according to a third embodiment of the present invention.
11 is a view of a refrigeration cycle according to a fourth embodiment of the present invention.
12 is a view of the flow of refrigerant in a refrigeration cycle according to a fourth embodiment of the present invention.
13 is a view of a refrigeration cycle according to a fifth embodiment of the present invention.
14 is a view of the flow of refrigerant in a refrigeration cycle according to a fifth embodiment of the present invention.
15 is a view of a refrigeration cycle according to a sixth embodiment of the present invention.
16 is a view of the flow of refrigerant in a refrigeration cycle according to a sixth embodiment of the present invention.
17 is a view of a refrigeration cycle according to a seventh embodiment of the present invention.
18 is a view of the flow of refrigerant in a refrigeration cycle according to a seventh embodiment of the present invention.
19 is a view of a refrigeration cycle according to an eighth embodiment of the present invention.
20 is a view of the flow of refrigerant in a refrigeration cycle according to an eighth embodiment of the present invention.
21 is a view of a refrigeration cycle according to a ninth embodiment of the present invention.
22 is a view of the flow of refrigerant in a refrigeration cycle according to a ninth embodiment of the present invention.
23 is a view of a refrigeration cycle according to a tenth embodiment of the present invention.
24 is a view of the flow of refrigerant in a refrigeration cycle according to a tenth embodiment of the present invention.

Hereinafter, embodiments of the present invention will be described in detail with reference to the accompanying drawings.

1 is a view of a refrigeration cycle according to a first embodiment of the present invention.

As shown in FIG. 1, the compressor 110, the condenser 120, the evaporator 130, the ejector 180, and the flow path switching device 190 are connected through a refrigerant pipe, thereby providing a closed loop refrigerant circuit.

In detail, the refrigeration cycle 100 includes a first refrigerant circuit, a second refrigerant circuit, and a third refrigerant circuit.

The first refrigerant circuit is configured so that the refrigerant discharged from the compressor 110 flows back to the compressor 110 through the condenser 120, the ejector 180, the first evaporator 140, and the second evaporator 150. The second refrigerant circuit is configured such that the refrigerant bypasses the first evaporator 140 in the first refrigerant circuit. That is, the first refrigerant circuit is provided to pass through the first evaporator 140 and the second evaporator 150, and in the second refrigerant circuit, only the second evaporator 150 is provided. The third refrigerant circuit is branched at a branch point S provided downstream of the condenser 120 in the first refrigerant circuit or the second refrigerant circuit, and the refrigerant passes through the expansion device 170 and the third evaporator 160 to the ejector ( 180). The refrigerant is provided to flow through any one of the first refrigerant circuit and the second refrigerant circuit and the third refrigerant circuit.

The third refrigerant circuit includes a 3a refrigerant circuit and a 3b refrigerant circuit. The expansion device 170 lowers the temperature and pressure of the liquid refrigerant. The expansion device 170 includes a first expansion device 171 provided upstream of the third evaporator 160 and a second expansion device 172 disposed in series with the first expansion device 171. The 3a refrigerant circuit is provided to pass through the first expansion device 171 provided upstream of the third evaporator 160, and the 3b refrigerant circuit is provided through the first expansion device 171 and the second expansion device 172. It is prepared to be.

The use of the first evaporator 140, the second evaporator 150, and the third evaporator 160 is not limited, but in the embodiment of the present invention, the first evaporator 140 is used in the refrigerating compartment of the refrigerator 80, and The 2 evaporator 150 and the third evaporator 160 may be used in the freezer of the refrigerator 80. That is, the first evaporator 140 may be referred to as the refrigerating chamber evaporator 130, and the second evaporator 150 and the third evaporator 160 may be referred to as the freezing chamber evaporator 130. The refrigerating chamber of the refrigerator 80 may be referred to as a first cooling chamber 91 and the freezing chamber of the refrigerator 80 may be referred to as a second cooling chamber 92. In addition, the second cooling chamber 92 may be provided to be formed at a lower temperature than the first cooling chamber 91.

The refrigeration cycle 100 may be provided to operate a full cooling mode and a refrigeration cooling mode.

The total cooling mode is an operation mode in which both the first cooling chamber 91 and the second cooling chamber 92 are cooled. That is, in the total cooling mode, the refrigerant is provided to flow through the first evaporator 140, the second evaporator 150, and the third evaporator 160. In the total cooling mode, the refrigerant is provided to flow through the first refrigerant circuit and the third refrigerant circuit. In detail, in the overall cooling mode, the refrigerant is provided to flow through the first refrigerant circuit and the 3a refrigerant circuit.

The refrigeration cooling mode is an operation mode for cooling the second cooling chamber 92. That is, in the refrigeration/cooling mode, the refrigerant is provided to flow through the second evaporator 150 and the third evaporator 160. In the refrigeration/cooling mode, the refrigerant is provided to flow through the second refrigerant circuit and the third refrigerant circuit. Specifically, in the refrigerant cooling mode, the refrigerant is provided to flow through the second refrigerant circuit and the 3b refrigerant circuit.

In the total cooling mode and the refrigerant cooling mode, since the number of evaporators 130 through which the refrigerant flows is different, it is necessary to adjust the refrigerant flow rate. To this end, the compressor 110 may include an inverter compressor. By controlling the refrigerant flow rate in the refrigerant circuit through the control of the rotation RPM of the inverter compressor, it is possible to switch between the total cooling mode and the refrigeration cooling mode.

Refrigerant flow control between the plurality of refrigerant circuits is performed through the flow path switching device 190. The flow path switching device 190 flows refrigerant into the first refrigerant circuit, the second refrigerant circuit, the 3a refrigerant circuit, and the 3b refrigerant circuit according to the temperature required in the first cooling chamber 91 and the second cooling chamber 92. Is prepared to switch

The flow path conversion device 190 includes a first flow path conversion device 191 and a second flow path conversion device 192.

The first flow path switching device 191 is provided to control a refrigerant flow between the first refrigerant circuit and the second refrigerant circuit. In detail, the refrigerant discharged from the ejector 180 is provided to flow through at least one of the first refrigerant circuit and the second refrigerant circuit.

In detail, the first flow path switching device 191 may alternatively select a first refrigerant circuit through which the refrigerant flows through the first evaporator 140 and the second evaporator 150 and a second refrigerant circuit through which the second evaporator 150 flows. It is arranged to move as an enemy.

The second flow path switching device 192 is provided downstream of the condenser 120 and is provided between the branch point S branching from the first refrigerant circuit or the second refrigerant circuit to the third refrigerant circuit, and the expansion device 170. The second flow path switching device 192 is provided to control a refrigerant flow between the 3a refrigerant circuit and the 3b refrigerant circuit. In detail, the refrigerant branching from the branch point S is provided to flow through at least one of the 3a refrigerant circuit and the 3b refrigerant circuit.

In detail, the second flow path switching device 192 includes a 3a refrigerant circuit through which the refrigerant flows through the first expansion device 171, and a 3b refrigerant through the first expansion device 171 and the second expansion device 172. It is provided to alternately move the circuit.

The flow path switching device 190 may include a 3-way valve. The first flow path switching device 191 may include a valve 1a (191a) for opening and closing a first refrigerant circuit, and a valve 1b 191b for opening and closing a second refrigerant circuit. The second flow path switching device 192 may include a 2a valve 192a for opening and closing the 3a refrigerant circuit and a 2b valve 192b for opening and closing the 3b refrigerant circuit.

The refrigeration cycle 100 drives a condenser 120, a plurality of blowing fans 121, 141, 151, and blowing fans 121, 141, 151 provided adjacent to the plurality of cooling chambers 91, 92. It includes a plurality of fan motors (122, 142, 152). In detail, the condenser blowing fan 121, the first cooling chamber blowing fan 141, the second cooling chamber blowing fan 151, and the condenser fan motor 122, the first cooling chamber fan motor 142, respectively, to drive the same, It includes a second cooling chamber fan motor 152.

In addition, a first defrost heater 143 and a second defrost heater 153 are provided on the surfaces of the first evaporator 140 and the second evaporator 150 to remove frost on the surface of the evaporator 130. I can.

The working refrigerant flowing through the refrigeration cycle 100 may include HC-based isobutane (R600a), propane (R290), HFC-based R134a, and HFO-based R1234yf. However, the type of refrigerant is not limited, and any refrigerant that can achieve a target temperature through heat exchange with the surroundings is satisfied.

The expansion device 170 may include a capillary tube, an electronic expansion valve (EV), and a capillary tube.

2 is a view of the flow of refrigerant in the refrigeration cycle according to the first embodiment of the present invention, and FIG. 3 is a view of the ejector of the refrigeration cycle according to the first embodiment of the present invention. It means the refrigerant flow in the total cooling mode, and (b) means the refrigerant flow in the refrigeration cooling mode.

The ejector 180 is provided to expand isentropically in the cooling device.

The ejector 180 may include a nozzle unit 181, a suction unit 183, a mixing unit 184, and a diffuser unit 185. The refrigerant discharged from the compressor 110 flows to the branch point S through the condenser 120. The refrigerant reaching the branch point S is divided into a main refrigerant flowing from the branch point S to the ejector 180 and a sub-refrigerant moving along the third refrigerant circuit and flows.

The main refrigerant passes through the nozzle part 181 and flows to the mixing part 184, and the sub-refrigerant flows along the third refrigerant circuit and is sucked into the suction part 183 of the ejector 180, and the main refrigerant flows through the mixing part 184. It is mixed with the refrigerant and discharged from the ejector 180 through the diffuser unit 185.

Based on the flow of the main refrigerant and the sub-refrigerant, the evaporator 130 may be classified into a main evaporator and a sub-evaporator. The main evaporator includes a first evaporator 140 provided in the first cooling chamber 91 and a second evaporator 150 provided in the second cooling chamber 92, and the sub-evaporator includes a second cooling chamber 92 It includes a third evaporator 160 provided in.

When the main refrigerant passes through the nozzle unit 181, isentropic expansion occurs, and the enthalpy difference before and after the nozzle unit 181 becomes the difference in speed of the main refrigerant, and the main refrigerant is ejected at high speed from the outlet of the nozzle unit 181. Make it possible.

In the diffuser unit 185, the velocity energy of the mixed refrigerant in which the main refrigerant and the sub-refrigerant are mixed is converted into pressure energy, thereby increasing the pressure. When the refrigerant passed through the ejector 180 through this process flows into the compressor 110, the compression work of the compressor 110 is reduced, thereby increasing the COP (Coefficient of Performance) of the refrigeration cycle 100.

The flow of refrigerant in the ejector 180 will be described.

The main refrigerant discharged from the condenser 120 flows into the inlet of the nozzle part 181 of the ejector 180. As the main refrigerant passes through the nozzle unit 181 in the ejector 180, the flow velocity of the main refrigerant becomes high and the pressure decreases.

The nozzle part 181 includes a nozzle body 181a, a nozzle inlet part 181b through which the main refrigerant is introduced, and a nozzle discharge part 181c through which the main refrigerant is discharged.

In the nozzle discharge unit 181c, the secondary refrigerant flowing in a state in which the pressure of the main refrigerant is lowered and flowing in the saturated gas state through the second evaporator 150 through the second refrigerant circuit or the third refrigerant circuit is higher than the saturation pressure. It is sucked into the suction unit 183 of the ejector 180 due to a pressure difference with the main refrigerant having a relatively low pressure.

The main refrigerant passed through the nozzle unit 181 and the sub-refrigerant sucked through the suction unit 183 are mixed in the mixing unit 184 of the ejector 180. As the mixed refrigerant passes through the fan-shaped diffuser 185 formed at the outlet of the ejector 180, the flow rate decreases and the pressure rises to flow into the first evaporator 140 or the second evaporator 150. . As the refrigerant is evaporated by absorbing heat from the surroundings while passing through the evaporator 130, the refrigerant at the outlet of the evaporator 130 becomes a saturated gas or supersaturated state, and is then sucked into the compressor 110.

In this way, in the cycle with the ejector 180, the pressure of the refrigerant sucked into the compressor 110 is increased compared to the cycle without the ejector 180, so that the refrigerant flowing into the compressor 110 reaches the condensation temperature. During compression, the work load of the compressor 110 decreases, and the COP (Coefficient of Performance, performance coefficient) of the entire cycle increases.

The ejector 180 may include a needle unit 187.

The needle unit 187 may include a needle portion 187a and a needle driving portion 187b. The needle portion 187a is provided so that the diameter of the cross section thereof is different in the longitudinal direction. The needle part 187a is provided so that one end thereof penetrates the nozzle inlet 181b. Through this configuration, the needle portion (187a) moves forward and backward through the nozzle inlet portion (181b) to the nozzle body (181a), so that the width of the nozzle inlet portion (181b) through which the refrigerant flows into the nozzle body (181a) can be finely adjusted. It is prepared to be able to.

The needle driving part 187b is provided at the other end of the needle unit 187 and provided so that the needle unit 187 moves forward and backward.

While passing through the ejector 180, the main refrigerant and the sub-refrigerant are combined. The ratio of the mass flow rate of the sub-refrigerant to the mass flow rate of the main refrigerant is called the entrainment ratio (ω),

Becomes.

The improvement of the performance of the refrigeration cycle 100 is caused by an increase in the pressure of the ejector 180, and is an index representing the performance of the ejector 180, and the pressure list ratio (PLR) is as follows. Is defined.

PLR=(P5-P6)/P6*100 [%]

The boosting rate of the ejector 180 has an inverse relationship with the suction ratio. In order to increase the COP of the refrigeration cycle 100, the suction amount must be reduced, but it is not easy to arbitrarily change the dryness value of the refrigerant passing through the ejector 180, and it is said that the suction amount is reduced by maintaining a low dryness value. Even so, the cooling capacity in the evaporator 130 decreases, making it difficult to improve the ultimate COP value.

Therefore, the first evaporator 140 and the second evaporator 150 are arranged like the first refrigerant circuit and the second refrigerant circuit, and the second evaporator 150 and the third evaporator 160 are placed in the same second cooling chamber 92 ), the second evaporator 150 supplements the cooling capacity even though the cooling capacity of the third evaporator 160 is insufficient by reducing the suction amount to improve the boosting rate of the ejector 180, 100) will be able to improve the COP.

Depending on the operating conditions, it can be divided into a total cooling mode that cools both the first cooling chamber 91, the refrigerating chamber, and the second cooling chamber 92, a freezer, and a refrigeration cooling mode that cools only the second cooling chamber 92. , This is due to the direction of the flow path of the flow path switching device 190.

First, the flow of the refrigeration cycle 100 in the total cooling mode will be described with reference to a Moliere diagram.

The compressor 110 sucks the refrigerant vapor of low temperature and low pressure and compresses it into superheated vapor of high temperature and high pressure (8→1). The high-temperature and high-pressure superheated steam passes through the condenser 120 and heats up through heat exchange with the surrounding air, while the refrigerant is condensed to change its phase to a liquid refrigerant or a two-phase refrigerant (1→2).

The refrigerant condensed in the condenser 120 is branched at the branch point S and divided into a main refrigerant and a sub refrigerant to flow.

The main refrigerant flows into the nozzle inlet 181b of the ejector 180. The main refrigerant introduced into the nozzle inlet 181b passes through the nozzle unit 181 of the ejector 180 and the pressure is strong according to the isentropic process, so that the phase change of the refrigerant occurs and becomes a two-phase refrigerant ( 2→3). The main refrigerant in the nozzle discharge portion 181c is in a state of high speed and low pressure.

The ejector 180 includes a nozzle discharge part 181c and a suction passage part 182 having a concentric circle shape. As the main refrigerant is in a high-speed and low-pressure state, the sub-refrigerant is also located on the same line as the nozzle discharge unit 181c and the refrigerant flow and passes through the suction passage unit 182 having the shape of a concentric circle, and becomes low pressure like the main refrigerant. The sub-refrigerant branched at the branch point S flows into the second flow path switching device 192. In the total cooling mode, the second flow path switching device 192 opens the 2a valve 192a and closes the 2b valve 192b, so that the sub-refrigerant passing through the second flow path switching device 192 is (2=9) It passes through the first expansion device 171 (9→10) and the third evaporator 160 (10→6). At this time, the cooling temperature of the third evaporator 160 may be about -19°C.

The sub-refrigerant passing through the third evaporator 160 is sucked in the suction unit 183 of the ejector 180 in a state of low pressure saturated steam. In this case, the suction force of the refrigerant is a force corresponding to the difference between the saturation pressure of the third evaporator 160 and the pressure of the suction passage part 182 which is the same pressure as the nozzle discharge part 181c. In general, since the pressure of the exposed discharge portion is smaller than the pressure in the suction portion 183, the sub-refrigerant is sucked into the flow of the main refrigerant (6→3').

In the mixing unit 184, momentum is transmitted by mixing the main refrigerant passing through the nozzle unit 181 and the sub-refrigerant passing through the suction unit 183 and passing through the suction passage unit 182. (3→4, 3′→ 4) As the flow rate of the refrigerant decreases through the diffuser unit 185, the pressure of the refrigerant increases by a certain portion (4→5').

The refrigerant boosted in this way is introduced into the first flow path switching device 191. In the total cooling mode, as the first flow path switching device 191 opens the first valve 1a (191a) and closes the valve 1b (191b), the refrigerant is transferred to the first evaporator 140 (5→7) and the second evaporator ( 150) (7 → 8).

The low-temperature and low-pressure refrigerant passing through the second evaporator 150 is sucked into the compressor 110 and compressed into high-temperature and high-pressure superheated steam (8→1).

Next, the flow of the refrigeration cycle 100 in the refrigeration cooling mode will be described with reference to the Moliere diagram.

The compressor 110 sucks the refrigerant vapor of low temperature and low pressure and compresses it into superheated vapor of high temperature and high pressure (8→1). The high-temperature and high-pressure superheated steam passes through the condenser 120 and heats up through heat exchange with the surrounding air, while the refrigerant is condensed to change its phase to a liquid refrigerant or a two-phase refrigerant (1→2).

The refrigerant condensed in the condenser 120 is branched at the branch point S and divided into a main refrigerant and a sub refrigerant to flow.

The main refrigerant flows into the nozzle inlet 181b of the ejector 180. The main refrigerant introduced into the nozzle inlet 181b passes through the nozzle unit 181 of the ejector 180 and the pressure is strong according to the isentropic process, so that the phase change of the refrigerant occurs and becomes a two-phase refrigerant ( 2→3). The main refrigerant in the nozzle discharge portion 181c is in a state of high speed and low pressure.

The suction passage part 182 having a concentric circle shape while being located in the cross section of the nozzle discharge part 181c is also at the same low pressure. The sub-refrigerant branched at the branch point S flows into the second flow path switching device 192. In the refrigeration/cooling mode, the 2a valve 192a is closed and the 2b valve 192b is opened in the second flow path switching device 192, so that the sub-refrigerant passing through the second flow path switching device 192 is transferred to the second expansion device ( 172) (2→9).

The sub-refrigerant passing through the second expansion device 172 passes through the first expansion device 171 (9→10) and the third evaporator 160 (10→6). In this case, the cooling temperature of the third evaporator 160 may be about -28°C, which is a lower cooling temperature than in the total cooling mode, since additional decompression occurs in the second expansion device 172. In addition, since the nozzle inlet 181b is also controlled by the needle unit 187, more decompression is generated than in the total cooling mode.

The sub-refrigerant passing through the third evaporator 160 is sucked in the suction unit 183 of the ejector 180 in a state of low pressure saturated steam. In this case, the suction force of the refrigerant is a force corresponding to the difference between the saturation pressure of the third evaporator 160 and the pressure of the suction passage part 182 which is the same pressure as the nozzle discharge part 181c. In general, since the pressure of the exposed discharge portion is smaller than the pressure in the suction portion 183, the sub-refrigerant is sucked into the flow of the main refrigerant (6→3').

In the mixing unit 184, momentum is transmitted by mixing the main refrigerant passing through the nozzle unit 181 and the sub-refrigerant passing through the suction unit 183 and passing through the suction passage unit 182. (3→4, 3'→ 4) As the flow rate of the refrigerant decreases through the diffuser unit 185, the pressure of the refrigerant increases by a certain portion (4→5').

The refrigerant boosted in this way is introduced into the first flow path switching device 191. In the refrigeration/cooling mode, as the first flow path switching device 191 closes the 1a valve 191a and opens the 1b valve 191b, the refrigerant passes through the first flow path switching device 191 (5=7), The second evaporator 150 (7→8) is passed.

The low-temperature and low-pressure refrigerant passing through the second evaporator 150 is sucked into the compressor 110 and compressed into high-temperature and high-pressure superheated steam (8→1).

4 is a diagram illustrating an operation of a partial configuration of a refrigeration cycle according to an operation mode according to the first embodiment of the present invention.

With reference to FIG. 4, the full cooling mode and the refrigeration cooling mode will be described, and further, the defrost mode will be described.

FIG. 4 is a diagram illustrating ON/OFF of the compressor 110, the first cooling chamber blowing fan 141, and the second cooling chamber blowing fan 151, and a first refrigerant opened to flow into the first refrigerant circuit and the 3a refrigerant circuit. The opening/closing states of the 1a valve 191a and the 2a valve 192a, and the 1b valve and the 2b valve 192b that are opened so that the refrigerant flows to the second refrigerant circuit and the 3b refrigerant circuit will be described.

When the compressor 110 starts starting in the total cooling mode, the first cooling chamber blowing fan 141 and the second cooling chamber blowing fan 151 are also operated, and the 1a valve 191a and the 2a valve ( 192a) is opened, and the 1b valve 191b and the 2b valve 192b are in a closed state.

Since the refrigerant flows through the first refrigerant circuit, it flows from the first evaporator 140 to the second evaporator 150 through the first flow path switching device 191. When the target temperature of the first cooling chamber 91 by the first evaporator 140 is first achieved, the refrigeration cooling mode is operated. The target temperature of the first cooling chamber 91 is not limited, but the temperature of the image is preferably 3°C. At this time, the temperature of the second cooling chamber 92 is not limited, but it is preferably a temperature below zero, and for example, it may be -18°C.

In the refrigeration cooling mode, the first cooling chamber blowing fan 141 is stopped, the 1a valve 191a and the 2a valve 192a are closed, and the 1b valve 191b and the 2b valve 192b are open. do. In the refrigeration/cooling mode, only the second cooling chamber 92 is cooled, and since the refrigerant flows through the second refrigerant circuit, it flows only to the second evaporator 150 through the first flow path switching device 191.

Since the number of the evaporators 130 flowing in the total cooling mode and the refrigeration cooling mode is different, the required refrigerant flow rate in the total cooling mode and the refrigerant flow rate required in the refrigeration cooling mode are different. Therefore, when switching from the total cooling mode to the refrigeration cooling mode, the flow rate of the refrigerant can be controlled by employing a variable-capacity inverter compressor to control the number of revolutions.

When the target temperature of the second cooling chamber 92 is reached, the defrost mode may be entered.

The target temperature of the second cooling chamber 92 in the refrigeration cooling mode is not limited, but it is preferably a temperature below zero, and for example, it may be -28°C lower than that of the second cooling chamber 92 in the total cooling mode. have.

In the defrost mode, the compressor 110 and the second cooling chamber blowing fan 151 are stopped, and only the first cooling chamber blowing fan 141 can operate. In addition, the 1a valve 191a and the 2a valve 192a may be opened, and the 1b valve 191b and the 2b valve 192b may be closed. That is, the flow path switching device 190 opens the 1a valve 191a and the 2a valve 192a so that the refrigerant flows through the first refrigerant circuit and the 3a refrigerant circuit. Through this configuration, the frost formed on the first evaporator 140 is defrosted by circulating air in the first cooling chamber 91. Moisture generated through the defrost mode may improve the humidity inside the refrigerator 80. In addition, vegetables in the refrigerator 80 may be freshly stored through moisture generated through the defrost mode.

5 is a control diagram of a cooling cycle according to the first embodiment of the present invention.

The refrigerator 80 according to an exemplary embodiment of the present invention provides various cooling modes through the control of the controller 60 such as a microcomputer. 5 is a block diagram of a control system centered on a control unit 60 provided in the refrigerator 80 according to an exemplary embodiment of the present invention. 5, a key input unit 52, a first cooling chamber temperature sensing unit 54, and a second cooling chamber temperature sensing unit 56 are connected to the input port of the control unit 60. The key input unit 52 is provided with a plurality of function keys, and these function keys include function keys related to setting operating conditions of the refrigerator 80 such as setting a cooling mode or setting a desired temperature. The first cooling chamber temperature sensing unit 54 and the second cooling chamber temperature sensing unit 56 sense the internal temperatures of the first cooling chamber 91 and the second cooling chamber 92, respectively, and provide them to the control unit 60 do.

The output port of the control unit 60 includes a compressor driving unit 62, a first cooling chamber blowing fan driving unit 64, a second cooling chamber blowing fan driving unit 66, a flow path switching device driving unit 68, and a defrost heater driving unit 72. , The display unit 70 is connected. Among them, the remaining components except for the display unit 70 are the compressor 110, the first cooling chamber fan motor 142, the second cooling chamber fan motor 152, and the 1a valve 191a of the first flow path switching device 191, respectively. ) And the 1b valve 191b, the 2a valve 192a and the 2b valve 192b of the second flow path switching device 192, and the defrost heater. The display unit 70 displays the operating state of the cooling device, various set values, and temperatures.

The control unit 60 controls the first flow path switching device 191 and the second flow path switching device 192 to control any one of the first refrigerant circuit and the second refrigerant circuit shown in FIG. 5, and the 3a refrigerant circuit. Various cooling modes are implemented by circulating the refrigerant through any one of the refrigerant circuits and 3b refrigerant circuits. Representative cooling modes that can be implemented in the refrigerator 80 according to an embodiment of the present invention include a first cooling mode, which is an overall cooling mode, and a second cooling mode, which is a refrigeration cooling mode. The total cooling mode is an operation mode for cooling both the first cooling chamber 91 and the second cooling chamber 92. The controller 60 opens the valve 1a of the first flow path switching device 191 and the valve 2a 192a of the second flow path switching device 192 to implement the overall cooling mode, and the overall cooling mode The refrigerant discharged from the condenser 120 flows through the first evaporator 140, the second evaporator 150, the third evaporator 160, and the first expansion device 171.

The refrigeration cooling mode is an operation mode in which only the second cooling chamber 92 is cooled alone. In the refrigeration/cooling mode, the controller 60 opens the 1b valve 191b of the first flow path switching device 191 and the 2b valve 192b of the second flow path switching device 192, and the condenser ( The discharged refrigerant of 120 flows through the second evaporator 150, the third evaporator 160, the first expansion device 171, and the second expansion device 172.

In cooling the first cooling chamber 91 and the second cooling chamber 92 through this configuration, initially, the entire cooling mode is operated, and when the temperature of the first cooling chamber 91 reaches a certain temperature, 2 It is possible to maximize cooling efficiency by switching to a refrigeration cooling mode in which only the cooling chamber 92 is cooled. In addition, the refrigerant boosted by the ejector 180 is sucked into the compressor 110 to reduce compression work. Furthermore, the flow rate of the refrigerant used in the refrigerant cooling mode is lower than that in the total cooling mode, and the difference in refrigerant flow rate can be controlled by the rotation speed of the inverter compressor, thereby enabling efficient operation.

Hereinafter, an example of a state in which the refrigeration cycle 100 is disposed inside the refrigerator 80 will be described.

6A and 6B are diagrams illustrating an arrangement of a refrigerator and a refrigeration cycle according to the first embodiment of the present invention.

The refrigerator 80 may include a main body 90 forming an external appearance, a first cooling chamber 91 and a second cooling chamber 92 and a machine room 93 provided inside the main body 90.

The main body 90 may be formed of a material having a heat insulation function to prevent heat exchange between the outside and the cooling chamber inside the main body 90. That is, the body 90 may include a heat insulating wall 90a formed of a heat insulating material. The first cooling chamber 91, the second cooling chamber 92, and the machine chamber 93 may be divided by insulating walls 90a, respectively.

The compressor 110, the condenser 120, the condenser blowing fan 121, and the condenser fan motor 122 may be disposed in the machine room 93. Through this arrangement, noise can be prevented from leaking out of the main body 90 and heat generated from the compressor 110 and the condenser 120 can be prevented from being transferred to the cooling chamber.

The first evaporator 140, the first cooling chamber blowing fan 141, and the first cooling chamber fan motor 142 are disposed in the first cooling chamber 91, and the second evaporator 150 and the third evaporator 160 ) And the second cooling chamber blowing fan 151 and the second cooling chamber fan motor 152 may be provided in the second cooling chamber 92.

The third evaporator 160 may be disposed downstream of the second evaporator 150 with respect to the air flow direction by the second cooling chamber blowing fan 151. Through this arrangement, the heat exchange efficiency of the third evaporator 160 formed at a lower temperature than the second evaporator 150 may be improved.

The ejector 180 may be provided under the third evaporator 160. The sub-refrigerant discharged from the third evaporator 160 is sucked into the suction unit 183 of the ejector 180, and the flow of the refrigerant can be smoothed by making the flow of the sub-refrigerant equal to the direction of gravity.

The ejector 180 may be provided on the heat insulating wall 90a to minimize heat loss due to changes in state and temperature inside the ejector 180. Through this arrangement, it is possible to minimize the occurrence of heat loss due to heat exchange of the ejector 180 with the surroundings.

The first flow path switching device 191 may be located close to the exit of the ejector 180 and may be disposed on the heat insulating wall 90a together with the ejector 180. In addition, as shown in the drawing, it may be disposed in the second cooling chamber 92. Through this arrangement, it is possible to prevent heat loss from occurring in the refrigerant passing through the first flow path switching device 191, but is not limited thereto and may be disposed in the first cooling chamber 91, and the first cooling chamber 91 ) And the second cooling chamber 92 may be disposed between.

Hereinafter, a refrigeration cycle and a refrigerator having the same according to a second embodiment of the present invention will be described.

7 is a diagram illustrating a refrigeration cycle according to a second embodiment of the present invention, and FIG. 8 is a diagram illustrating a flow of refrigerant in a refrigeration cycle according to a second embodiment of the present invention. Figure 8 (a) means the refrigerant flow in the overall cooling mode, (b) means the refrigerant flow in the refrigeration cooling mode.

For the same configuration as in the first embodiment, detailed descriptions thereof will be omitted.

The refrigeration cycle 200 includes a first refrigerant circuit, a second refrigerant circuit, and a third refrigerant circuit.

The first refrigerant circuit is configured such that the refrigerant discharged from the compressor 210 flows back to the compressor 210 through the condenser 220, the ejector 280, the first evaporator 240, and the second evaporator 250. The second refrigerant circuit is configured such that the refrigerant bypasses the first evaporator 240 in the first refrigerant circuit. That is, in the first refrigerant circuit, it is provided to pass through the first evaporator 240 and the second evaporator 250, and in the second refrigerant circuit, it is provided to pass only the second evaporator 250. The third refrigerant circuit is branched at a branch point S provided downstream of the condenser 220 in the first refrigerant circuit or the second refrigerant circuit, and the ejector 280 through the expansion device 270 and the third evaporator 260 Is configured to join with. The refrigerant is provided to flow through any one of the first refrigerant circuit and the second refrigerant circuit and the third refrigerant circuit.

The third refrigerant circuit includes a 3a refrigerant circuit and a 3b refrigerant circuit. The expansion device 270 includes a first expansion device 271 provided upstream of the third evaporator 260 and a second expansion device 272 disposed in series with the first expansion device 271. The 3a refrigerant circuit is provided to pass through the first expansion device 271 provided upstream of the third evaporator 260, and the 3b refrigerant circuit is provided through the first expansion device 271 and the second expansion device 272. It is prepared to be.

The first evaporator 240 may be disposed in the first cooling chamber 91, and the second evaporator 250 and the third evaporator 260 may be disposed in the second cooling chamber 92.

The flow path conversion device 290 includes a first flow path conversion device 291 and a second flow path conversion device 292. The first flow path switching device 291 may include a valve 1a (291a) for opening and closing the first refrigerant circuit, and a valve 1b (291b) for opening and closing the second refrigerant circuit. The second flow path switching device 292 may include a 2a valve 292a that opens and closes the 3a refrigerant circuit, and a 2b valve 292b that opens and closes the 3b refrigerant circuit.

The refrigeration cycle 200 includes a condenser 220 and a plurality of blowing fans provided adjacent to the plurality of cooling chambers, and a plurality of fan motors for driving the blowing fans. In detail, the condenser blowing fan 221, the first cooling chamber blowing fan 241, the second cooling chamber blowing fan 251, and a condenser fan motor 222, a first cooling chamber fan motor 242, respectively, to drive the same, It includes a second cooling chamber fan motor 252.

In addition, a first defrost heater 243 and a second defrost heater 253 are provided on the surfaces of the first evaporator 240 and the second evaporator 250 to remove frost on the surface of the evaporator 230. I can.

The ejector 280 may include a nozzle unit 281, a suction unit 283, a mixing unit 284, and a diffuser unit 285. The nozzle unit 281 may include a nozzle body 281a, a nozzle inlet portion 281b, and a nozzle discharge portion 281c. The ejector 280 includes a nozzle discharge part 281c and a suction passage part 282 having a concentric circle shape.

The refrigeration cycle 200 may include a heat exchanger.

The heat exchanger is provided to exchange heat with each other between a partial section of the third refrigerant circuit and an inlet of the compressor 210. Saturated gas or supersaturated refrigerant is preferably introduced into the compressor 210, but some liquid refrigerant may be introduced, and the condenser 220 to prevent deterioration and damage of the compressor 210 due to this. A heat exchanger may be included so that heat exchange occurs between the outlet of) and the inlet of the compressor 210.

The heat exchanger may include a first heat exchanger 295a provided at the first expansion device 271 in the third refrigerant circuit, and a second heat exchanger 295b provided at the inlet of the compressor 210, and the first By transferring heat from the heat exchanger 295a to the second heat exchanger 295b, it is possible to overheat the refrigerant flowing into the compressor 210.

The first expansion device 271 and the heat exchanger may be integrally configured. The heat exchanger includes a SLHX heat exchanger (Suction Line heat exchanger). The superheat degree of the refrigerant sucked into the compressor 210 can be secured through a SLHX heat exchanger (Suction Line heat exchanger), so that damage to the compressor 210 due to the inflow of the liquid refrigerant is prevented.

This process will be described with reference to the Moliere diagram.

Compared to the Moliere diagram in the first embodiment, the process of passing through the first heat exchanger 295a and the first expansion device 271 (9→10), and the compressor 210 from the discharge portion of the second evaporator 250 There is a difference in the process (8"→8) passing through the second heat exchanger 295b, which is a process flowing into the furnace.

That is, by transferring heat from the first heat exchanger 295a to the second heat exchanger 295b, the enthalpy in the state 10 passing through the first heat exchanger 295a and the first expansion device 271 is reduced. In the first embodiment, the enthalpy is smaller than the enthalpy in the state 10 passing through the first expansion device 271, and the amount of change in the enthalpy decrease according to this state change is transmitted as an increase change amount of the enthalpy of the refrigerant flowing into the compressor 210. do. That is, the enthalpy in the state 8 passing through the second heat exchanger 295b is greater than the enthalpy in the state passing through the second heat exchanger 295b in the first embodiment.

Through this process, the cooling capacity of the third evaporator 260 can be increased, and the superheat degree of the refrigerant sucked into the compressor 210 can be secured, thereby preventing damage to the compressor 210 and improving the reliability. do.

Hereinafter, a refrigeration cycle according to a third embodiment of the present invention and a refrigerator having the same will be described.

9 is a view of a refrigeration cycle according to a third embodiment of the present invention, and FIG. 10 is a view of a flow of refrigerant in a refrigeration cycle according to a third embodiment of the present invention. Figure 10 (a) refers to the refrigerant flow in the overall cooling mode, and (b) refers to the refrigerant flow in the refrigeration cooling mode.

For the same configuration as in the first embodiment, detailed descriptions thereof will be omitted.

The refrigeration cycle 300 includes a first refrigerant circuit, a second refrigerant circuit, and a third refrigerant circuit.

The first refrigerant circuit is configured such that the refrigerant discharged from the compressor 310 flows back to the compressor 310 through the condenser 320, the ejector 380, the first evaporator 340, and the second evaporator 350. The second refrigerant circuit is configured such that the refrigerant bypasses the first evaporator 340 in the first refrigerant circuit. That is, the first refrigerant circuit is provided to pass through the first evaporator 340 and the second evaporator (350), and in the second refrigerant circuit, only the second evaporator 350 is provided. The third refrigerant circuit is branched at a branch point S provided downstream of the condenser 320 in the first refrigerant circuit or the second refrigerant circuit, and the ejector 380 through the expansion device 370 and the third evaporator 360 Is configured to join with. The refrigerant is provided to flow through one of the first refrigerant circuit and the second refrigerant circuit and the third refrigerant circuit.

The third refrigerant circuit includes a 3a refrigerant circuit and a 3b refrigerant circuit. The expansion device 370 includes a first expansion device 371 provided upstream of the third evaporator 360 and a second expansion device 372 disposed in series with the first expansion device 371. The 3a refrigerant circuit is provided to pass through the first expansion device 371 provided upstream of the third evaporator 360, and the 3b refrigerant circuit is provided through the first expansion device 371 and the second expansion device 372. It is prepared to be.

The first evaporator 340 may be disposed in the first cooling chamber 91, and the second evaporator 350 and the third evaporator 360 may be disposed in the second cooling chamber 92.

The flow path switching device 390 includes a first flow path switching device 391 and a second flow path switching device 392. The first flow path switching device 391 may include a valve 1a (391a) for opening and closing a first refrigerant circuit, and a valve 1b (391b) for opening and closing a second refrigerant circuit. The second flow path switching device 392 may include a 2a valve 392a that opens and closes the 3a refrigerant circuit, and a 2b valve 392b that opens and closes the 3b refrigerant circuit.

The refrigeration cycle 300 includes a condenser 320 and a plurality of blowing fans provided adjacent to the plurality of cooling chambers, and a plurality of fan motors for driving the blowing fans. In detail, the condenser blowing fan 321, the first cooling chamber blowing fan 341, the second cooling chamber blowing fan 351, and a condenser fan motor 322, a first cooling chamber fan motor 342, respectively, to drive the same, And a second cooling chamber fan motor 352.

In addition, a first defrost heater 343 and a second defrost heater 353 are provided on the surfaces of the first evaporator 340 and the second evaporator 350 so as to remove frost on the surface of the evaporator 330. I can.

The ejector 380 may include a nozzle part 381, a suction part 383, a mixing part 384, and a diffuser part 385. The nozzle portion 381 may include a nozzle body 381a, a nozzle inlet portion 381b, and a nozzle discharge portion 381c. The ejector 380 includes a nozzle discharge part 381c and a suction passage part 382 having a concentric circle shape.

The refrigeration cycle 300 may include a heat exchanger.

The heat exchanger is provided to exchange heat with each other between a partial section of the third refrigerant circuit and an inlet of the compressor 310. Saturated gas or supersaturated refrigerant is preferably introduced into the compressor 310, but some liquid refrigerant may be introduced, and the condenser 320 to prevent performance degradation and damage of the compressor 310 due to this. A heat exchanger may be included so that heat exchange occurs between the outlet of) and the inlet of the compressor 310.

The heat exchanger includes a first heat exchanger 395a provided at the first expansion device 371 and the second expansion device 372 in the third refrigerant circuit, and a second heat exchanger 395b provided at the inlet of the compressor 310 It may include, and by transferring heat from the first heat exchanger 395a to the second heat exchanger 395b, it is possible to overheat the refrigerant flowing into the compressor 310.

The first expansion device 371, the second expansion device 372 and the heat exchanger may be integrally configured. The heat exchanger includes a SLHX heat exchanger (Suction Line heat exchanger). The superheat degree of the refrigerant sucked into the compressor 310 can be secured through a SLHX heat exchanger (Suction Line heat exchanger), so that damage to the compressor 310 due to the inflow of the liquid refrigerant is prevented.

This process will be described with reference to the Moliere diagram.

Compared to the Moliere diagram in the first embodiment, the process of passing through the first heat exchanger 395a, the first expansion device 371 and the second expansion device 372 (2→10), and the second evaporator 350 There is a difference in the process (8"→8) of passing through the second heat exchanger 395b, which is a process of flowing into the compressor 310 from the discharge part of.

That is, by transferring heat from the first heat exchanger 395a to the second heat exchanger 395b, the state passes through the first heat exchanger 395a, the first expansion device 371, and the second expansion device 372. The enthalpy at (10) becomes smaller than the enthalpy at the state (10) passed through the first expansion device 371 in the first embodiment, and the amount of change in the decrease in enthalpy according to this state change is introduced into the compressor 310 It is transmitted as an increasing change in the enthalpy of the refrigerant The enthalpy in the state 8 passing through the second heat exchanger 395b is greater than the enthalpy in the state passing through the second heat exchanger 395b in the first embodiment.

Through this process, the cooling capacity of the third evaporator 360 can be increased, and the superheat degree of the refrigerant sucked into the compressor 310 can be secured, thereby preventing damage to the compressor 310 and improving the reliability. do.

Hereinafter, a refrigeration cycle according to a fourth embodiment of the present invention and a refrigerator having the same will be described.

11 is a view of a refrigeration cycle according to a fourth embodiment of the present invention, and FIG. 12 is a view of a flow of refrigerant in a refrigeration cycle according to a fourth embodiment of the present invention. Figure 12 (a) means the refrigerant flow in the overall cooling mode, (b) means the refrigerant flow in the refrigeration cooling mode.

For the same configuration as in the first embodiment, detailed descriptions thereof will be omitted.

The refrigeration cycle 400 includes a first refrigerant circuit, a second refrigerant circuit, and a third refrigerant circuit.

The first refrigerant circuit is configured such that the refrigerant discharged from the compressor 410 flows back to the compressor 410 through the condenser 420, the ejector 480, the first evaporator 440, and the second evaporator 450. The second refrigerant circuit is configured such that the refrigerant bypasses the first evaporator 440 in the first refrigerant circuit. That is, the first refrigerant circuit is provided to pass through the first evaporator 440 and the second evaporator (450), and in the second refrigerant circuit, only the second evaporator 450 is provided. The third refrigerant circuit is branched at a branch point S provided downstream of the condenser 420 in the first refrigerant circuit or the second refrigerant circuit, and the ejector 480 passes through the expansion device 470 and the third evaporator 460. Is configured to join with. The refrigerant is provided to flow through any one of the first refrigerant circuit and the second refrigerant circuit and the third refrigerant circuit.

The third refrigerant circuit includes a 3a refrigerant circuit and a 3b refrigerant circuit. The expansion device 470 includes a first expansion device 471 provided upstream of the third evaporator 460 and a second expansion device 472 disposed in series with the first expansion device 471. The 3a refrigerant circuit is provided to pass through the first expansion device 471 provided upstream of the third evaporator 460, and the 3b refrigerant circuit is provided through the first expansion device 471 and the second expansion device 472. It is prepared to be.

The first evaporator 440 may be disposed in the first cooling chamber 91, and the second evaporator 450 and the third evaporator 460 may be disposed in the second cooling chamber 92.

The flow path switching device 490 includes a first flow path switching device 491 and a second flow path switching device 492. The first flow path switching device 491 may include a valve 1a 491a that opens and closes the first refrigerant circuit, and a valve 1b 491b that opens and closes the second refrigerant circuit. The second flow path switching device 492 may include a 2a valve 492a for opening and closing the 3a refrigerant circuit and a 2b valve 492b for opening and closing the 3b refrigerant circuit.

The refrigeration cycle 400 includes a condenser 420 and a plurality of blowing fans provided adjacent to the plurality of cooling chambers, and a plurality of fan motors for driving the blowing fans. In detail, the condenser blowing fan 421, the first cooling chamber blowing fan 441, the second cooling chamber blowing fan 451, and the condenser fan motor 422, the first cooling chamber fan motor 442, respectively, to drive the same, And a second cooling chamber fan motor 452.

In addition, a first defrost heater 443 and a second defrost heater 453 are provided on the surfaces of the first evaporator 440 and the second evaporator 450 to remove frost on the surface of the evaporator 430. I can.

The ejector 480 may include a nozzle unit 481, a suction unit 483, a mixing unit 484, and a diffuser unit 485. The nozzle portion 481 may include a nozzle body 481a, a nozzle inlet portion 481b, and a nozzle discharge portion 481c. The ejector 480 includes a nozzle discharge part 481c and a suction passage part 482 having a concentric circle shape.

The refrigeration cycle 400 may include a heat exchanger.

The heat exchanger is provided to exchange heat between a partial section of the third refrigerant circuit and an inlet of the compressor 410, and between an inlet of the compressor 410 and a discharge portion of the condenser 420, respectively. It is preferable that a saturated gas or a supersaturated refrigerant flows into the compressor 410, but some liquid refrigerant can flow into the condenser 420 to prevent deterioration and damage of the compressor 410 due to this. A heat exchanger may be included so that heat exchange occurs between the outlet of) and the inlet of the compressor 410.

The heat exchanger includes a first heat exchanger 495a provided in the first expansion device 471 in a third refrigerant circuit, a second heat exchanger 495b provided at the inlet of the compressor 410, and a third heat exchanger 496a. , It may include a fourth heat exchanger (496b) provided in the discharge portion of the condenser 420. The heat from the first heat exchanger 495a is transferred to the second heat exchanger 495b, and the heat from the fourth heat exchanger 496b is transferred to the third heat exchanger 496a to flow into the compressor 410. It becomes possible to overheat the refrigerant. The second heat exchanger 495b and the third heat exchanger 496a are shown and described separately, but may be formed integrally.

The first expansion device 471 and the heat exchanger may be integrally configured. The heat exchanger includes a SLHX heat exchanger (Suction Line heat exchanger). The superheat degree of the refrigerant sucked into the compressor 410 through the SLHX heat exchanger (Suction Line heat exchanger) can be secured, so that damage to the compressor 410 due to the inflow of the liquid refrigerant is prevented.

This process will be described with reference to the Moliere diagram.

Compared to the Moliere diagram in the first embodiment, the process of passing through the first heat exchanger 495a and the first expansion device 471 (9→10), and the refrigerant discharged from the condenser 420 is converted into a fourth heat exchanger ( The process of going through 496b) (2"→2) and the process of passing through the second heat exchanger 495b and the third heat exchanger 496a, which are the processes flowing into the compressor 410 from the discharge part of the second evaporator 450 (8"→8) there is a difference.

That is, by transferring heat from the first heat exchanger 495a to the second heat exchanger 495b, the enthalpy in the state 10 passing through the first heat exchanger 495a and the first expansion device 471 is reduced. In the first embodiment, the enthalpy is smaller than the enthalpy in the state 10 passed through the first expansion device 471, and the amount of change in the decrease in enthalpy according to this state change is transmitted as an increase change amount of the enthalpy of the refrigerant flowing into the compressor 410. do. In addition, by transferring heat from the fourth heat exchanger 496b to the third heat exchanger 496a, the enthalpy in the state (2) passing through the condenser 420 and the fourth heat exchanger 496b is reduced in the first embodiment. It becomes smaller than the enthalpy in the state (2) passing through the condenser 420 of, and the decrease change amount of the enthalpy according to the state change is transmitted as an increase change amount of the enthalpy of the refrigerant flowing into the compressor 410. That is, the enthalpy in the state 8 passing through the second heat exchanger 495b is greater than the enthalpy in the state passing through the second heat exchanger 495b in the first embodiment.

Through this process, the cooling capacity of the third evaporator 460 can be increased, and the superheat degree of the refrigerant sucked into the compressor 410 can be secured, thereby preventing damage to the compressor 410 and improving reliability. do.

Hereinafter, a refrigeration cycle and a refrigerator having the same according to a fifth embodiment of the present invention will be described.

13 is a diagram illustrating a refrigeration cycle according to a fifth embodiment of the present invention, and FIG. 14 is a diagram illustrating a flow of a refrigerant in a refrigeration cycle according to a fifth embodiment of the present invention. 14(a) means the refrigerant flow in the total cooling mode, and (b) means the refrigerant flow in the refrigeration/cooling mode.

For the same configuration as in the first embodiment, detailed descriptions thereof will be omitted.

The refrigeration cycle 500 includes a first refrigerant circuit, a second refrigerant circuit, and a third refrigerant circuit.

The first refrigerant circuit is configured such that the refrigerant discharged from the compressor 510 flows back to the compressor 510 through the condenser 520, the ejector 580, the first evaporator 540, and the second evaporator 550. The second refrigerant circuit is configured such that the refrigerant bypasses the first evaporator 540 in the first refrigerant circuit. That is, in the first refrigerant circuit, it is provided to pass through the first evaporator 540 and the second evaporator (550), and in the second refrigerant circuit, it is provided to pass only the second evaporator 550. The third refrigerant circuit is branched at a branch point S provided downstream of the condenser 520 in the first refrigerant circuit or the second refrigerant circuit, and the ejector 580 through the expansion device 570 and the third evaporator 560 Is configured to join with. The refrigerant is provided to flow through any one of the first refrigerant circuit and the second refrigerant circuit and the third refrigerant circuit.

The third refrigerant circuit includes a 3a refrigerant circuit and a 3b refrigerant circuit. The expansion device 570 includes a first expansion device 571 provided upstream of the third evaporator 560 and a second expansion device 572 disposed in series with the first expansion device 571. The 3a refrigerant circuit is provided to pass through the first expansion device 571 provided upstream of the third evaporator 560, and the 3b refrigerant circuit is provided through the first expansion device 571 and the second expansion device 572. It is prepared to be.

The first evaporator 540 may be disposed in the first cooling chamber 91, and the second evaporator 550 and the third evaporator 560 may be disposed in the second cooling chamber 92.

The flow path conversion device 590 includes a first flow path conversion device 591 and a second flow path conversion device 592. The first flow path switching device 591 may include a valve 1a 591a that opens and closes the first refrigerant circuit, and a valve 1b 591b that opens and closes the second refrigerant circuit. The second flow path switching device 592 may include a 2a valve 592a for opening and closing the 3a refrigerant circuit and a 2b valve 592b for opening and closing the 3b refrigerant circuit.

The refrigeration cycle 500 includes a condenser 520 and a plurality of blowing fans provided adjacent to the plurality of cooling chambers, and a plurality of fan motors for driving the blowing fans. In detail, the condenser blowing fan 521, the first cooling chamber blowing fan 541, the second cooling chamber blowing fan 551, and the condenser fan motor 522, the first cooling chamber fan motor 542, respectively, to drive the same, And a second cooling chamber fan motor 552.

In addition, a first defrost heater 543 and a second defrost heater 553 are respectively provided on the surfaces of the first evaporator 540 and the second evaporator 550 to remove frost on the surface of the evaporator 530. I can.

The ejector 580 may include a nozzle part 581, a suction part 583, a mixing part 584, and a diffuser part 585. The nozzle portion 581 may include a nozzle body 581a, a nozzle inlet portion 581b, and a nozzle discharge portion 581c. The ejector 580 includes a nozzle discharge portion 581c and a suction passage portion 582 having a concentric circle shape.

The refrigeration cycle 500 may include a heat exchanger.

The heat exchanger is provided to exchange heat between a partial section of the third refrigerant circuit and an inlet of the compressor 510, and between an inlet of the compressor 510 and a discharge portion of the condenser 520, respectively. It is preferable that a saturated gas or a supersaturated refrigerant flows into the compressor 510, but some liquid refrigerant can flow into the condenser 520 to prevent deterioration and damage of the compressor 510. A heat exchanger may be included so that heat exchange occurs between the outlet of) and the inlet of the compressor 510.

The heat exchanger includes a first heat exchanger 595a provided in the first expansion device 571 and the second expansion device 572 in the third refrigerant circuit, and a second heat exchanger 595b provided at the inlet of the compressor 510 And a third heat exchanger 596a, and a fourth heat exchanger 596b provided at a discharge portion of the condenser 520. The heat from the first heat exchanger 595a is transferred to the second heat exchanger 595b, and the heat from the fourth heat exchanger 596b is transferred to the third heat exchanger 596a to flow into the compressor 510. It becomes possible to overheat the refrigerant. The second heat exchanger 595b and the third heat exchanger 596a are shown and described separately, but may be formed integrally.

The first expansion device 571, the second expansion device 572, and the heat exchanger may be integrally configured. The heat exchanger includes a SLHX heat exchanger (Suction Line heat exchanger). The superheat degree of the refrigerant sucked into the compressor 510 through the SLHX heat exchanger (Suction Line heat exchanger) can be secured, so that damage to the compressor 510 due to the inflow of the liquid refrigerant is prevented.

This process will be described with reference to the Moliere diagram.

Compared to the Moliere diagram in the first embodiment, the process of passing through the first heat exchanger 595a, the first expansion device 571 and the second expansion device 572 (9→10), and discharge from the condenser 520 The second heat exchanger 595b and the third process in which the refrigerant is passed through the fourth heat exchanger 596b (2"→2), and flows into the compressor 510 from the discharge part of the second evaporator 550 There is a difference in the process (8"→8) passing through the heat exchanger 596a.

That is, by transferring heat from the first heat exchanger 595a to the second heat exchanger 595b, the state has passed through the first heat exchanger 595a, the first expansion device 571 and the second expansion device 572 The enthalpy at (10) becomes smaller than the enthalpy at the state (10) passed through the first expansion device 571 in the first embodiment, and the amount of change in the decrease in enthalpy according to this state change is introduced into the compressor 510 It is transmitted as an increasing amount of change in the enthalpy of refrigerant. In addition, by transferring heat from the fourth heat exchanger 596b to the third heat exchanger 596a, the enthalpy in the state (2) passing through the condenser 520 and the fourth heat exchanger 596b is reduced in the first embodiment. It becomes smaller than the enthalpy in the state (2) passing through the condenser 520 of, and the amount of change in the decrease of the enthalpy according to this state change is transmitted as an increase change amount of the enthalpy of the refrigerant flowing into the compressor 510. That is, the enthalpy in the state 8 passing through the second heat exchanger 595b is greater than the enthalpy in the state passing through the second heat exchanger 595b in the first embodiment.

Through this process, the cooling capacity of the third evaporator 560 can be increased, and the superheat degree of the refrigerant sucked into the compressor 510 can be secured, so that damage to the compressor 510 can be prevented and reliability can be improved. do.

Hereinafter, a refrigeration cycle according to a sixth embodiment of the present invention and a refrigerator having the same will be described.

15 is a diagram illustrating a refrigeration cycle according to a sixth embodiment of the present invention, and FIG. 16 is a diagram illustrating a flow of a refrigerant in a refrigeration cycle according to a sixth embodiment of the present invention. Figure 16 (a) means the refrigerant flow in the total cooling mode, (b) means the refrigerant flow in the refrigeration cooling mode.

For the same configuration as in the first embodiment, detailed descriptions thereof will be omitted.

The refrigeration cycle 600 includes a first refrigerant circuit, a second refrigerant circuit, and a third refrigerant circuit.

The first refrigerant circuit is configured such that the refrigerant discharged from the compressor 610 flows back to the compressor 610 through the condenser 620, the ejector 680, the first evaporator 640, and the second evaporator 650. The second refrigerant circuit is configured such that the refrigerant bypasses the first evaporator 640 in the first refrigerant circuit. That is, in the first refrigerant circuit, it is provided to pass through the first evaporator 640 and the second evaporator 650, and in the second refrigerant circuit, it is provided to pass only the second evaporator 650. The third refrigerant circuit is branched at a branch point S provided downstream of the condenser 620 in the first refrigerant circuit or the second refrigerant circuit, and the ejector 680 through the expansion device 670 and the third evaporator 660 Is configured to join with. The refrigerant is provided to flow through any one of the first refrigerant circuit and the second refrigerant circuit and the third refrigerant circuit.

The third refrigerant circuit includes a 3a refrigerant circuit and a 3b refrigerant circuit. The expansion device 670 includes a first expansion device 671 provided upstream of the third evaporator 660 and a second expansion device 672 disposed in series with the first expansion device 671. The 3a refrigerant circuit is provided to pass through the first expansion device 671 provided upstream of the third evaporator 660, and the 3b refrigerant circuit is provided through the first expansion device 671 and the second expansion device 672. It is prepared to be.

The first evaporator 640 may be disposed in the first cooling chamber 91, and the second evaporator 650 and the third evaporator 660 may be disposed in the second cooling chamber 92.

The flow path switching device 690 includes a first flow path switching device 691 and a second flow path switching device 692. The first flow path switching device 691 may include a valve 1a 691a for opening and closing the first refrigerant circuit, and a valve 1b 691b for opening and closing the second refrigerant circuit. The second flow path switching device 692 may include a 2a valve 692a for opening and closing the 3a refrigerant circuit, and a 2b valve 692b for opening and closing the 3b refrigerant circuit.

The refrigeration cycle 600 includes a condenser 620 and a plurality of blowing fans provided adjacent to the plurality of cooling chambers, and a plurality of fan motors for driving the blowing fans. In detail, the condenser blowing fan 621, the first cooling chamber blowing fan 641, the second cooling chamber blowing fan 651, and a condenser fan motor 622, a first cooling chamber fan motor 642, respectively, to drive the same, And a second cooling chamber fan motor 652.

In addition, a first defrost heater 643 and a second defrost heater 653 are respectively provided on the surfaces of the first evaporator 640 and the second evaporator 650 to remove frost on the surface of the evaporator 630. I can.

The ejector 680 may include a nozzle part 681, a suction part 683, a mixing part 684, and a diffuser part 685. The nozzle part 681 may include a nozzle body 681a, a nozzle inlet 681b, and a nozzle discharge part 681c. The ejector 680 includes a nozzle discharge portion 681c and a suction passage portion 682 having a concentric circle shape.

The refrigeration cycle 600 may include a heat exchanger.

The heat exchanger is provided to exchange heat between a partial section of the third refrigerant circuit and an inlet of the compressor 610, and between an inlet of the compressor 610 and an inlet of the ejector 680, respectively. Saturated gas or supersaturated refrigerant is preferably introduced into the compressor 610, but some liquid refrigerant may be introduced, and the condenser 620 to prevent deterioration and damage of the compressor 610 due to this. A heat exchanger may be included so that heat exchange occurs between the outlet of) and the inlet of the compressor 610.

The heat exchanger includes a first heat exchanger 695a provided at the first expansion device 671 in the third refrigerant circuit, a second heat exchanger 695b provided at the inlet of the compressor 610, and a third heat exchanger 696a. , It may include a fourth heat exchanger 696b provided in the inlet of the ejector 680. Heat from the first heat exchanger (695a) is transferred to the second heat exchanger (695b), and heat from the fourth heat exchanger (696b) is transferred to the third heat exchanger (696a) to flow into the compressor (610). It becomes possible to overheat the refrigerant. The second heat exchanger 695b and the third heat exchanger 696a are shown and described separately, but they may be formed integrally.

The first expansion device 671 and the heat exchanger may be integrally configured. The heat exchanger includes a SLHX heat exchanger (Suction Line heat exchanger). The superheat degree of the refrigerant sucked into the compressor 610 through the SLHX heat exchanger (Suction Line heat exchanger) can be secured, so that damage to the compressor 610 due to the inflow of the liquid refrigerant is prevented.

This process will be described with reference to the Moliere diagram.

Compared to the Moliere diagram in the first embodiment, the process of passing through the first heat exchanger 695a and the first expansion device 671 (9→10), and the refrigerant flowing into the ejector 680 is a fourth heat exchanger ( The process of going through 696b) (2"→2) and the process of passing through the second heat exchanger 695b and the third heat exchanger 696a, which are the processes flowing into the compressor 610 from the discharge part of the second evaporator 650 (8"→8) there is a difference.

That is, by transferring heat from the first heat exchanger 695a to the second heat exchanger 695b, the enthalpy in the state 10 passing through the first heat exchanger 695a and the first expansion device 671 is reduced. In the first embodiment, the enthalpy is smaller than the enthalpy in the state 10 passed through the first expansion device 671, and the amount of change in the enthalpy decrease according to this state change is transmitted as an increase change amount of the enthalpy of the refrigerant flowing into the compressor 610. do. In addition, by transferring heat from the fourth heat exchanger 696b to the third heat exchanger 696a, the enthalpy in the state (2) passing through the condenser 620 and the fourth heat exchanger 696b is reduced in the first embodiment. It becomes smaller than the enthalpy in the state (2) passing through the condenser 620 of, and the decrease change amount of the enthalpy according to this state change is transmitted as an increase change amount of the enthalpy of the refrigerant flowing into the compressor 610. That is, the enthalpy in the state 8 passing through the second heat exchanger 695b is greater than the enthalpy in the state passing through the second heat exchanger 695b in the first embodiment.

Through this process, the cooling capacity of the third evaporator 660 can be increased, and the superheat degree of the refrigerant sucked into the compressor 610 can be secured, so that damage to the compressor 610 can be prevented and reliability can be improved. do.

Hereinafter, a refrigeration cycle according to a seventh embodiment of the present invention and a refrigerator having the same will be described.

FIG. 17 is a view of a refrigeration cycle according to a seventh embodiment of the present invention, and FIG. 18 is a view of a refrigerant flow in a refrigeration cycle according to a seventh embodiment of the present invention. Figure 18 (a) means the refrigerant flow in the total cooling mode, (b) means the refrigerant flow in the refrigeration cooling mode.

For the same configuration as in the first embodiment, detailed descriptions thereof will be omitted.

The refrigeration cycle 700 includes a first refrigerant circuit, a second refrigerant circuit, and a third refrigerant circuit.

The first refrigerant circuit is configured such that the refrigerant discharged from the compressor 710 flows back to the compressor 710 through the condenser 720, the ejector 780, the first evaporator 740, and the second evaporator 750. The second refrigerant circuit is configured such that the refrigerant bypasses the first evaporator 740 in the first refrigerant circuit. That is, in the first refrigerant circuit, it is provided to pass through the first evaporator 740 and the second evaporator (750), and in the second refrigerant circuit, it is provided so as to pass only the second evaporator 750. The third refrigerant circuit is branched at a branch point S provided downstream of the condenser 720 in the first refrigerant circuit or the second refrigerant circuit, and the ejector 780 passes through the expansion device 770 and the third evaporator 760. Is configured to join with. The refrigerant is provided to flow through any one of the first refrigerant circuit and the second refrigerant circuit and the third refrigerant circuit.

The third refrigerant circuit includes a 3a refrigerant circuit and a 3b refrigerant circuit. The expansion device 770 includes a first expansion device 771 provided upstream of the third evaporator 760 and a second expansion device 772 disposed in series with the first expansion device 771. The 3a refrigerant circuit is provided to pass through the first expansion device 771 provided upstream of the third evaporator 760, and the 3b refrigerant circuit is provided through the first expansion device 771 and the second expansion device 772. It is prepared to be.

The first evaporator 740 may be disposed in the first cooling chamber 91, and the second evaporator 750 and the third evaporator 760 may be disposed in the second cooling chamber 92.

The flow path conversion device 790 includes a first flow path conversion device 791 and a second flow path conversion device 792. The first flow path switching device 791 may include a valve 1a 791a that opens and closes the first refrigerant circuit, and a valve 1b 791b that opens and closes the second refrigerant circuit. The second flow path switching device 792 may include a 2a valve 792a for opening and closing the 3a refrigerant circuit and a 2b valve 792b for opening and closing the 3b refrigerant circuit.

The refrigeration cycle 700 includes a condenser 720 and a plurality of blowing fans provided adjacent to the plurality of cooling chambers, and a plurality of fan motors for driving the blowing fans. In detail, the condenser blowing fan 721, the first cooling chamber blowing fan 741, the second cooling chamber blowing fan 751, and the condenser fan motor 722, the first cooling chamber fan motor 742, respectively, to drive the same, It includes a second cooling chamber fan motor (752).

In addition, a first defrost heater 743 and a second defrost heater 753 are provided on the surfaces of the first evaporator 740 and the second evaporator 750 to remove frost on the surface of the evaporator 730. I can.

The ejector 780 may include a nozzle part 781, a suction part 783, a mixing part 784, and a diffuser part 785. The nozzle portion 781 may include a nozzle body 781a, a nozzle inlet portion 781b, and a nozzle discharge portion 781c. The ejector 780 includes a nozzle discharge portion 781c and a suction passage portion 782 having a concentric circle shape.

The refrigeration cycle 700 may include a heat exchanger.

The heat exchanger is provided to exchange heat between a partial section of the third refrigerant circuit and an inlet of the compressor 710, and between an inlet of the compressor 710 and an inlet of the ejector 780, respectively. It is preferable that a saturated gas or a supersaturated refrigerant flows into the compressor 710, but some liquid refrigerant may flow into the compressor 710, and the condenser 720 to prevent performance degradation and damage of the compressor 710 due to this. A heat exchanger may be included to generate heat exchange between the outlet of) and the inlet of the compressor 710.

The heat exchanger includes a first heat exchanger 795a provided in the first expansion device 771 and the second expansion device 772 in the third refrigerant circuit, and a second heat exchanger 795b provided at the inlet of the compressor 710 And a third heat exchanger 796a and a fourth heat exchanger 796b provided at an inlet of the ejector 780. The heat from the first heat exchanger 795a is transferred to the second heat exchanger 795b, and the heat from the fourth heat exchanger 796b is transferred to the third heat exchanger 796a to flow into the compressor 710. It becomes possible to overheat the refrigerant. Although the second heat exchanger 795b and the third heat exchanger 796a are shown and described separately, they may be integrally formed.

The first expansion device 771, the second expansion device 772, and the heat exchanger may be integrally configured. The heat exchanger includes a SLHX heat exchanger (Suction Line heat exchanger). Since the superheat degree of the refrigerant sucked into the compressor 710 can be secured through a SLHX heat exchanger (Suction Line heat exchanger), damage to the compressor 710 due to the inflow of the liquid refrigerant is prevented.

This process will be described with reference to the Moliere diagram.

Compared to the Moliere diagram in the first embodiment, the process of passing through the first heat exchanger 795a, the first expansion device 771, and the second expansion device 772 (9→10), and the flow into the ejector 780 The second heat exchanger 795b and the third process of refrigerant passing through the fourth heat exchanger 796b (2"→2), and the process of flowing into the compressor 710 from the discharge portion of the second evaporator 750 There is a difference in the process (8"→8) passing through the heat exchanger 796a.

That is, by transferring heat from the first heat exchanger 795a to the second heat exchanger 795b, the state has passed through the first heat exchanger 795a, the first expansion device 771 and the second expansion device 772 The enthalpy at (10) becomes smaller than the enthalpy at the state (10) passed through the first expansion device 771 in the first embodiment, and the amount of change in enthalpy decrease according to this state change is introduced into the compressor 710 It is transmitted as an increasing amount of change in the enthalpy of refrigerant. In addition, by transferring heat from the fourth heat exchanger 796b to the third heat exchanger 796a, the enthalpy in the state (2) passing through the condenser 720 and the fourth heat exchanger 796b is reduced in the first embodiment. It becomes smaller than the enthalpy in the state (2) passing through the condenser 720 of, and the decrease change amount of the enthalpy according to this state change is transmitted as an increase change amount of the enthalpy of the refrigerant flowing into the compressor 710. That is, the enthalpy of the state 8 passing through the second heat exchanger 795b is greater than the enthalpy of the state passing through the second heat exchanger 795b in the first embodiment.

Through this process, the cooling capacity of the third evaporator 760 can be increased, and the superheat degree of the refrigerant sucked into the compressor 710 can be secured, thereby preventing damage to the compressor 710 and improving the reliability. do.

Hereinafter, a refrigeration cycle according to an eighth embodiment of the present invention and a refrigerator having the same will be described.

19 is a view of a refrigeration cycle according to an eighth embodiment of the present invention, and FIG. 20 is a view of a refrigerant flow in a refrigeration cycle according to an eighth embodiment of the present invention. Figure 20 (a) means the refrigerant flow in the overall cooling mode, (b) means the refrigerant flow in the refrigeration cooling mode.

For the same configuration as in the first embodiment, detailed descriptions thereof will be omitted.

The refrigeration cycle 800 includes a first refrigerant circuit, a second refrigerant circuit, and a third refrigerant circuit.

The first refrigerant circuit is configured such that the refrigerant discharged from the compressor 810 flows back to the compressor 810 through the condenser 820, the ejector 880, the first evaporator 840, and the second evaporator 850. The second refrigerant circuit is configured such that the refrigerant bypasses the first evaporator 840 in the first refrigerant circuit. That is, in the first refrigerant circuit, it is provided to pass through the first evaporator 840 and the second evaporator 850, and in the second refrigerant circuit, it is provided to pass only the second evaporator 850. The third refrigerant circuit is branched at a branch point S provided downstream of the condenser 820 in the first refrigerant circuit or the second refrigerant circuit, and the ejector 880 passes through the expansion device 870 and the third evaporator 860. Is configured to join with. The refrigerant is provided to flow through any one of the first refrigerant circuit and the second refrigerant circuit and the third refrigerant circuit.

The third refrigerant circuit includes a 3a refrigerant circuit and a 3b refrigerant circuit. The expansion device 870 includes a first expansion device 871 provided upstream of the third evaporator 860 and a second expansion device 872 disposed in series with the first expansion device 871. The 3a refrigerant circuit is provided to pass through the first expansion device 871 provided upstream of the third evaporator 860, and the 3b refrigerant circuit is provided through the first expansion device 871 and the second expansion device 872. It is prepared to be.

The first evaporator 840 may be disposed in the first cooling chamber 91, and the second evaporator 850 and the third evaporator 860 may be disposed in the second cooling chamber 92.

The flow path conversion device 890 includes a first flow path conversion device 891 and a second flow path conversion device 892. The first flow path switching device 891 may include a valve 1a (891a) for opening and closing the first refrigerant circuit, and a valve 1b (891b) for opening and closing the second refrigerant circuit. The second flow path switching device 892 may include a 2a valve 892a for opening and closing a 3a refrigerant circuit, and a 2b valve 892b for opening and closing a 3b refrigerant circuit.

The refrigeration cycle 800 includes a condenser 820 and a plurality of blowing fans provided adjacent to the plurality of cooling chambers, and a plurality of fan motors driving the blowing fans. In detail, the condenser blowing fan 821, the first cooling chamber blowing fan 841, the second cooling chamber blowing fan 851, and the condenser fan motor 822, the first cooling chamber fan motor 842, respectively, to drive the same, And a second cooling chamber fan motor 852.

In addition, a first defrost heater 843 and a second defrost heater 853 are respectively provided on the surfaces of the first evaporator 840 and the second evaporator 850 to remove frost on the surface of the evaporator 830. I can.

The ejector 880 may include a nozzle part 881, a suction part 883, a mixing part 884, and a diffuser part 885. The nozzle part 881 may include a nozzle body 881a, a nozzle inlet part 881b, and a nozzle discharge part 881c. The ejector 880 includes a nozzle discharge part 881c and a suction passage part 882 having a concentric circle shape.

The refrigeration cycle 800 may include a heat exchanger.

The heat exchanger is provided to exchange heat between the inlet of the compressor 810 and the discharge portion of the condenser 820, respectively. It is preferable that a saturated gas or a supersaturated refrigerant flows into the compressor 810, but some liquid refrigerant may flow into the compressor 810, and the condenser 820 to prevent performance degradation and damage of the compressor 810 due to this. A heat exchanger may be included so that heat exchange occurs between the outlet of) and the inlet of the compressor 810.

The heat exchanger may include a first heat exchanger 895a provided at an inlet part of the compressor 810 and a second heat exchanger 895b provided at a discharge part of the condenser 820. Heat from the second heat exchanger 895b is transferred to the first heat exchanger 895a to overheat the refrigerant flowing into the compressor 810.

The refrigeration cycle 800 is provided in the discharge portion of the condenser 820 and includes third expansion devices 873 and 870 for lowering the temperature and pressure of the refrigerant discharged from the condenser 820. The third expansion devices 873 and 870 may be provided between the condenser 820 and the ejector 880. When the refrigerant flowing into the nozzle unit 881 of the ejector 880 is in a two-phase state, the efficiency of the ejector 880 is improved, so that the third expansion devices 873 and 870 contain liquid refrigerant discharged from the condenser 820. It is prepared so that the quality can be increased.

The third expansion devices 873 and 870 and the heat exchanger may be integrally configured. The heat exchanger includes a SLHX heat exchanger (Suction Line heat exchanger). Since the superheat degree of the refrigerant sucked into the compressor 810 can be secured through the SLHX heat exchanger (Suction Line heat exchanger), damage to the compressor 810 due to the inflow of the liquid refrigerant is prevented.

This process will be described with reference to the Moliere diagram.

Compared to the Moliere diagram in the first embodiment, the process in which the refrigerant discharged from the condenser 820 passes through the second heat exchanger 895b (2"→2), and the compressor from the discharge part of the second evaporator 850 ( There is a difference in a process (8"→8) passing through the first heat exchanger 895a, which is a process flowing into the 810.

That is, by transferring heat from the second heat exchanger 895b to the first heat exchanger 895a, the enthalpy in the state (2) passing through the condenser 820 and the second heat exchanger 895b is the first embodiment. It becomes smaller than the enthalpy in the state (2) passing through the condenser 820 in, and the amount of change in the decrease of the enthalpy according to the state change is transmitted as an increase change amount of the enthalpy of the refrigerant flowing into the compressor 810. That is, the enthalpy of the state 8 passing through the second heat exchanger 895b is greater than the enthalpy 8 of the state passing through the second heat exchanger 895b in the first embodiment.

Through this process, the cooling capacity of the third evaporator 860 can be increased, and the superheat degree of the refrigerant sucked into the compressor 810 can be secured, so that damage to the compressor 810 can be prevented and reliability can be improved. do.

Hereinafter, a refrigeration cycle according to a ninth embodiment of the present invention and a refrigerator having the same will be described.

21 is a view of a refrigeration cycle according to a ninth embodiment of the present invention, and FIG. 22 is a view of a refrigerant flow in a refrigeration cycle according to a ninth embodiment of the present invention. Figure 22 (a) refers to the refrigerant flow in the overall cooling mode, (b) refers to the refrigerant flow in the refrigeration cooling mode.

For the same configuration as in the first embodiment, detailed descriptions thereof will be omitted.

The refrigeration cycle 900 includes a first refrigerant circuit, a second refrigerant circuit, and a third refrigerant circuit.

The first refrigerant circuit is configured such that the refrigerant discharged from the compressor 910 flows back to the compressor 910 through the condenser 920, the ejector 980, and the first evaporator 940. The second refrigerant circuit is configured such that the refrigerant passes through a second evaporator 950 disposed in parallel with the first evaporator 940 in the first refrigerant circuit. That is, the first refrigerant circuit is provided to pass only the first evaporator 940, and the second refrigerant circuit is provided to pass only the second evaporator 950. The third refrigerant circuit is branched at a branch point S provided downstream of the condenser 920 in the first refrigerant circuit or the second refrigerant circuit, and the ejector 980 is passed through the expansion device 970 and the third evaporator 960. Is configured to join with. The refrigerant is provided to flow through any one of the first refrigerant circuit and the second refrigerant circuit and the third refrigerant circuit.

The third refrigerant circuit includes a 3a refrigerant circuit and a 3b refrigerant circuit. The expansion device 970 includes a first expansion device 971 provided upstream of the third evaporator 960 and a second expansion device 972 disposed in series with the first expansion device 971. The 3a refrigerant circuit is provided to pass through the first expansion device 971 provided upstream of the third evaporator 960, and the 3b refrigerant circuit is provided through the first expansion device 971 and the second expansion device 972. It is prepared to be.

The first evaporator 940 may be disposed in the first cooling chamber 91, and the second evaporator 950 and the third evaporator 960 may be disposed in the second cooling chamber 92.

The flow path switching device 990 includes a first flow path switching device 991 and a second flow path switching device 992. The first flow path switching device 991 may include a valve 1a (991a) for opening and closing the first refrigerant circuit, and a valve 1b (991b) for opening and closing the second refrigerant circuit. The second flow path switching device 992 may include a 2a valve 992a for opening and closing the 3a refrigerant circuit and a 2b valve 992b for opening and closing the 3b refrigerant circuit.

In this embodiment, unlike in the first embodiment, the refrigerant is provided to alternatively pass through the first evaporator 940 and the second evaporator 950 by the first flow path switching device 991. Through this configuration, a refrigerant cooling mode in which the refrigerant flows through the first refrigerant circuit and the 3a refrigerant circuit, and a refrigeration mode in which the refrigerant flows through the second refrigerant circuit and the 3b refrigerant circuit are included. The operation in the defrost mode is the same as in the first embodiment.

In the present embodiment, since the first cooling chamber 91 and the second cooling chamber 92 can be selectively intensively cooled through the refrigeration cycle 900, cooling efficiency can be improved during intensive cooling.

The refrigeration cycle 900 includes a condenser 920 and a plurality of blowing fans provided adjacent to the plurality of cooling chambers, and a plurality of fan motors driving the blowing fans. In detail, the condenser blowing fan 921, the first cooling chamber blowing fan 941, the second cooling chamber blowing fan 951, and the condenser fan motor 922, the first cooling chamber fan motor 942, respectively, to drive the same, It includes a second cooling chamber fan motor 952.

In addition, a first defrost heater 943 and a second defrost heater 953 are respectively provided on the surfaces of the first evaporator 940 and the second evaporator 950 to remove frost on the surface of the evaporator 930. I can.

The ejector 980 may include a nozzle unit 981, a suction unit 983, a mixing unit 984, and a diffuser unit 985. The nozzle portion 981 may include a nozzle body 981a, a nozzle inlet portion 981b, and a nozzle discharge portion 981c. The ejector 980 includes a nozzle discharge part 981c and a suction passage part 982 having a concentric circle shape.

This process will be described with reference to the Moliere diagram.

Compared to the Moliere diagram in the first embodiment, the refrigerant is discharged from the ejector 980 in the refrigeration/cooling mode and passes through the first refrigerant circuit passing through the first evaporator 940 by the first flow path switching device 991 (5→7 in Fig.??) and a process in which the refrigerant is discharged from the ejector 980 in the refrigeration/cooling mode and passes through the second refrigerant circuit passing through the second evaporator 950 by the first flow path switching device 991 There is a difference in (Fig. 5→7).

That is, since the first cooling chamber 91 and the second cooling chamber 92 can be selectively cooled, intensive cooling can be performed in a cooling chamber requiring cooling.

Hereinafter, a refrigeration cycle according to a tenth embodiment of the present invention and a refrigerator having the same will be described.

FIG. 23 is a view of a refrigeration cycle according to a tenth embodiment of the present invention, and FIG. 24 is a view of a refrigerant flow in a refrigeration cycle according to a tenth embodiment of the present invention.

For the same configuration as in the first embodiment, detailed descriptions thereof will be omitted.

The refrigeration cycle 1000 includes a first refrigerant circuit and a second refrigerant circuit.

The first refrigerant circuit is configured such that the refrigerant discharged from the compressor 1010 flows back to the compressor 1010 through the condenser 1020, the first expansion device 1071, and the first evaporator 1040.

The second refrigerant circuit bypasses the first expansion device 1071 and the first evaporator 1040 from the downstream of the condenser 1020 in the first refrigerant circuit, and the ejector 1080, the second evaporator 1050, and the third It is configured to flow back to the compressor 1010 via the evaporator 1060 and the second expansion device 1072.

The second refrigerant circuit is branched from the upstream of the ejector 1080 in the second refrigerant circuit 2a flowing into the compressor 1010 through the ejector 1080 and the second evaporator 1050, and the second expansion device ( 1072 and a 2b refrigerant circuit flowing into the suction part 1083 of the ejector 1080 through the third evaporator 1060.

The first evaporator 1040 may be provided to cool the first cooling chamber 91, and the second evaporator 1050 and the third evaporator 1060 may be provided to cool the second cooling chamber 92. The second cooling chamber 92 may be formed to have a lower temperature than the first cooling chamber 91, and the first cooling chamber 91 is a refrigerating chamber of the refrigerator 80, and the second cooling chamber 92 is a refrigerator ( 80) may mean a freezer.

The refrigeration cycle 1000 may be provided to operate a refrigeration cooling mode and a refrigeration cooling mode.

The refrigeration cooling mode is an operation mode for cooling the first cooling chamber 91. That is, in the refrigeration/cooling mode, the refrigerant flows only in the first evaporator 1040. In the refrigeration cooling mode, the refrigerant is provided to flow through the first refrigerant circuit.

The refrigeration cooling mode is an operation mode for cooling the second cooling chamber 92. That is, in the refrigeration/cooling mode, the refrigerant is provided to flow through the second evaporator 1050 and the third evaporator 1060. In the refrigeration/cooling mode, the refrigerant is provided to flow through the second refrigerant circuit.

Since the number of evaporators 1030 through which the refrigerant flows is different in the refrigerant cooling mode and the refrigerant cooling mode, it is necessary to adjust the refrigerant flow rate. To this end, the compressor 1010 may include an inverter compressor. By controlling the refrigerant flow rate in the refrigerant circuit through the control of the rotation RPM of the inverter compressor, it is possible to switch between the refrigeration cooling mode and the refrigeration cooling mode.

The flow path switching device 1091 is provided to control a refrigerant flow between the first refrigerant circuit and the second refrigerant circuit. In detail, the refrigerant discharged from the condenser 1020 is provided to flow through one of the first refrigerant circuit and the second refrigerant circuit.

In detail, the flow path switching device 1091 alternatively includes a first refrigerant circuit through which the refrigerant flows through the first evaporator 1040 and a second refrigerant circuit through which the second evaporator 1050 and the third evaporator 1060 flow. It is arranged to move.

The flow path switching device 1091 may include a 3-way valve. The flow path switching device 1091 may include a first valve 1091a that opens and closes the first refrigerant circuit, and a second valve 1091b that opens and closes the second refrigerant circuit.

The ejector 1080 may include a nozzle unit 1081, a suction unit 1083, a mixing unit 1084, and a diffuser unit 1085. The nozzle unit 1081 may include a nozzle body 1081a, a nozzle inlet 1081b, and a nozzle discharge unit 1081c. The ejector 1080 includes a nozzle discharge portion 1081c and a suction passage portion 1082 having a concentric circle shape.

The refrigeration cycle 1000 may include a heat exchanger.

The heat exchanger is provided to exchange heat between the inlet of the compressor 1010 and the discharge part of the condenser 1020, respectively. It is preferable that a saturated gas or a supersaturated refrigerant flows into the compressor 1010, but some liquid refrigerant may flow into the compressor 1010, and the condenser 1020 to prevent deterioration and damage of the compressor 1010 due to this. A heat exchanger may be included so that heat exchange occurs between the outlet of) and the inlet of the compressor 1010.

The heat exchanger includes a first heat exchanger 1095a disposed downstream from the first evaporator 1040 in the first refrigerant circuit, and a first heat exchanger 1095a disposed downstream of the condenser 1020 in the first refrigerant circuit and heat exchange with the first heat exchanger 1095a. It may include a second heat exchanger (1095b). In addition, the heat exchanger is provided in a third heat exchanger 1096a disposed downstream from the second evaporator 1050 in the 2a refrigerant circuit, and upstream of the third evaporator 1060 in the 2b refrigerant circuit, and the third heat exchanger 1096a ) May include a fourth heat exchanger (1096b) for heat exchange.

The second heat exchanger 1095b and the first expansion device 1071 may be integrally configured, and the fourth heat exchanger 1096b and the second expansion device 1072 may be integrally configured. The heat exchanger includes a SLHX (Suction Line heat exchanger). Since the superheat degree of the refrigerant sucked into the compressor 1010 can be secured through the SLHX heat exchanger (Suction Line heat exchanger), damage to the compressor 1010 due to the inflow of the liquid refrigerant is prevented.

This process will be described with reference to the Moliere diagram.

Depending on the operating conditions, it can be divided into a refrigeration cooling mode that cools the refrigerating chamber (the first cooling chamber 91) and a refrigeration cooling mode that cools the freezing chamber (the second cooling chamber 92). It is caused by the flow direction.

First, the flow of the refrigeration cycle 1000 in the refrigeration cooling mode will be described with reference to a Moliere diagram.

The compressor 1010 sucks low-temperature and low-pressure refrigerant vapor and compresses it into high-temperature and high-pressure superheated steam (6"→5). The high-temperature and high-pressure superheated steam passes through the condenser 1020 and heats up through heat exchange with the surrounding air. The refrigerant is condensed and the phase is changed to a liquid refrigerant or a two-phase refrigerant (5→1).

In the refrigeration/cooling mode, the refrigerant condensed in the condenser 1020 flows through the first refrigerant circuit while the first valve is opened and the second valve is closed in the flow path switching device 1091. The refrigerant passing through the flow path switching device 1091 passes through the first expansion device 1071 and the temperature and pressure are lowered. In addition, heat is transferred from the second heat exchanger 1095b provided integrally with the first expansion device 1071 to the first heat exchanger 1095a (1→9→10).

The refrigerant passed through the first expansion device 1071 passes through the first evaporator 1040 and cools the refrigerating chamber, which is the first cooling chamber 91 (10→6). The refrigerant passing through the first evaporator 1040 passes through the first heat exchanger 1095a, becomes an overheated refrigerant (6→6"), and flows back into the compressor 1010 to form a refrigeration cycle 1000.

Next, the flow of the refrigeration cycle 1000 in the refrigeration/cooling mode will be described with reference to a Moliere diagram.

The compressor 1010 sucks low-temperature and low-pressure refrigerant vapor and compresses it into high-temperature and high-pressure superheated steam (4"→5). The high-temperature and high-pressure superheated steam passes through the condenser 1020 and heats the surrounding air through heat exchange. The refrigerant is condensed and the phase is changed to a liquid refrigerant or a two-phase refrigerant (5→1).

Since the refrigerant is in the refrigeration cooling mode, the refrigerant condensed in the condenser 1020 flows through the second refrigerant circuit as the first valve is closed and the second valve is opened in the flow path switching device 1091. The refrigerant passing through the flow path switching device 1091 is divided into a 2a refrigerant circuit and a 2b refrigerant circuit and flows.

The main refrigerant flowing through the 2a refrigerant circuit flows into the nozzle inlet 1081b of the ejector 1080. The main refrigerant introduced into the nozzle inlet 1081b passes through the nozzle unit 1081 of the ejector 1080 and decreases in pressure along the isentropic process, resulting in a phase change of the refrigerant to become a two-phase refrigerant (1→1' ). The main refrigerant in the nozzle discharge portion 1081c is in a state of high speed and low pressure.

The suction passage portion 1082 having the shape of a concentric circle while being positioned in a cross section on the same line as the nozzle discharge portion 1081c also has the same low pressure. The sub-refrigerant branched at the branch point (S). passes through the second expansion device 1072 to reduce the temperature and pressure of the refrigerant, and passes through the fourth heat exchanger 1096b to transfer heat to the third heat exchanger 1096a. Becomes (1→7→8).

The sub refrigerant passes through the third evaporator 1060 and absorbs heat from the second cooling chamber 92 to cool the second cooling chamber 92 (8→2). The sub-refrigerant passing through the third evaporator 1060 is sucked in the suction unit 1083 of the ejector 1080. In this case, the suction force of the refrigerant is a force corresponding to the difference between the saturation pressure of the third evaporator 1060 and the pressure of the suction passage part 1082 which is the same pressure as the nozzle discharge part 1081c. In general, since the pressure of the exposed discharge portion is less than the pressure in the suction portion 1083, the sub-refrigerant is sucked into the flow of the main refrigerant (2→2').

In the mixing unit 1084, momentum is transmitted by mixing the main refrigerant passed through the nozzle unit 1081 and the sub-refrigerant sucked into the suction passage unit 1082 of the suction unit 1083 (1'→3', 2' → 3'), as the flow velocity of the refrigerant through the diffuser unit 1085 decreases, the pressure of the refrigerant increases by a certain portion (3' → 3).

The refrigerant boosted in this way passes through the second evaporator 1050 and cools the second cooling chamber 92 (3→4). Thereafter, the refrigerant passes through the third heat exchanger 1096a, receives heat transferred from the fourth heat exchanger 1096b, is overheated (4→4"), and flows back into the compressor 1010 to form a refrigeration cycle 1000. do.

In the above, specific embodiments have been illustrated and described. However, it is not limited only to the above-described embodiments, and those of ordinary skill in the technical field to which the invention pertains will be able to perform various changes without departing from the gist of the technical idea of the invention described in the following claims. .

80: refrigerator 90: main body
100: refrigeration cycle 110: compressor
120: condenser 130: evaporator
140: first evaporator 150: second evaporator
160: third evaporator 170: expansion device
171: first expansion device 172: second expansion device
180: ejector 181: nozzle unit
182: suction passage part 183: suction part
184: mixing unit 185: diffuser unit
187: needle unit 190: flow path switching device
191: first flow path switching device 192: second flow path switching device
194: heat exchanger

Claims (30)

A first refrigerant circuit configured to flow to the compressor through a condenser, an ejector, a first evaporator disposed in the first cooling chamber, and a second evaporator disposed in the second cooling chamber;
A second refrigerant circuit configured such that the refrigerant bypasses the first evaporator in the first refrigerant circuit;
Branched at a branch point provided downstream of the condenser in at least one of the first refrigerant circuit and the second refrigerant circuit, the refrigerant merges into the ejector through an expansion device and a third evaporator disposed in the second cooling chamber. Includes; a third refrigerant circuit configured to be
The expansion device,
Including; a first expansion device and a second expansion device arranged in series with the first expansion device,
The third refrigerant circuit,
A 3a refrigerant circuit provided to pass through the first expansion device provided upstream of the third evaporator;
And a 3b refrigerant circuit provided to pass through the first expansion device and the second expansion device, and
In the overall cooling mode for cooling the first cooling chamber and the second cooling chamber, the refrigerant flows through the first refrigerant circuit and the 3a refrigerant circuit,
A refrigerant flow through the second refrigerant circuit and the 3b refrigerant circuit in a refrigeration cooling mode in which the second cooling chamber is cooled to a lower temperature than the total cooling mode. The method of claim 1,
A refrigerant cycle, characterized in that the refrigerant is provided to flow through any one of the first refrigerant circuit and the second refrigerant circuit and the third refrigerant circuit. delete delete delete delete delete The method of claim 1,
The second cooling chamber,
Including; a blowing fan provided for air flow therein,
The third evaporator,
A refrigeration cycle, characterized in that disposed downstream of the second evaporator with respect to the air flow direction by the blowing fan. The method of claim 1,
The refrigerant discharged from the condenser,
A main refrigerant flowing into the ejector through the first refrigerant circuit or the second refrigerant circuit;
And a sub-refrigerant branching at the branch point and flowing through a third refrigerant circuit to merge with the main refrigerant in the ejector. The method of claim 1,
A first flow path switching device provided to allow the refrigerant discharged from the ejector to flow through at least one of the first refrigerant circuit and the second refrigerant circuit;
And a second flow path switching device configured to allow the refrigerant branching from the branch point to the third refrigerant circuit to flow through any one of the 3a refrigerant circuit or the 3b refrigerant circuit. cycle. The method of claim 1,
The ejector,
A refrigeration cycle, characterized in that the refrigerant discharged from the condenser and the refrigerant discharged from the third evaporator are mixed and boosted and introduced into the compressor. The method of claim 1,
The ejector,
A nozzle part provided to expand the refrigerant discharged from the condenser under reduced pressure;
A suction unit for sucking the refrigerant discharged from the third evaporator;
A mixing unit in which the refrigerant introduced into the nozzle unit and the refrigerant introduced into the suction unit are mixed;
And a diffuser part provided to boost the refrigerant mixed in the mixing part. The method of claim 12,
The nozzle part,
And a nozzle body, a nozzle inlet portion through which refrigerant flows into the nozzle body, and a nozzle discharge portion formed to have a larger width than the nozzle inlet portion and discharge refrigerant from the nozzle body,
The ejector,
A refrigeration cycle comprising: a needle portion formed in a cross-section that is variable with respect to the longitudinal direction, and is provided to be advanced and retracted in the nozzle inlet. The method of claim 1,
And a first heat exchanger for exchanging heat between the first expansion device and the suction part of the compressor so that the refrigerant sucked into the compressor is overheated. The method of claim 14,
And a second heat exchanger for exchanging heat between the suction part of the compressor and the discharge part of the condenser. The method of claim 14,
And a second heat exchanger for exchanging heat between the suction unit of the compressor and a point downstream of the branch point in the first refrigerant circuit or the second refrigerant circuit. The method of claim 1,
And a first heat exchanger for exchanging heat between the first expansion device, the second expansion device, and the suction part of the compressor so that the refrigerant sucked into the compressor is overheated. The method of claim 17,
And a second heat exchanger for exchanging heat between the suction part of the compressor and the discharge part of the condenser. The method of claim 17,
And a second heat exchanger for exchanging heat between the suction unit of the compressor and a point downstream of the branch point in the first refrigerant circuit or the second refrigerant circuit. The method of claim 1,
Further comprising; a third expansion device provided on the discharge portion of the condenser,
And a first heat exchanger for exchanging heat between the third expansion device and the suction part of the compressor. The method of claim 1,
And a first heat exchanger for exchanging heat between the suction part of the compressor and a point downstream of the branch point in the first refrigerant circuit or the second refrigerant circuit. The method of claim 1,
The expansion device is a refrigeration cycle including any one of a capillary tube, an electronic expansion valve (EV), and a capillary tube. compressor;
A condenser for condensing the refrigerant discharged from the compressor;
An ejector through which a main refrigerant, which is at least a part of the refrigerant discharged from the condenser, flows in;
A first evaporator provided in the first cooling chamber, and a second evaporator provided in a second cooling chamber having a lower temperature than the first cooling chamber, and the refrigerant discharged from the ejector flows in and heat exchange with the surroundings to the compressor. A main evaporator for discharging a refrigerant;
An expansion device for moving the remaining sub-refrigerant among the refrigerant discharged from the condenser, the expansion device including a first expansion device and a second expansion device arranged in series with the first expansion device;
A sub-evaporator configured to have a third evaporator provided in the second cooling chamber, heat-exchanging with the surroundings to pass the sub-refrigerant passing through the expansion device, and discharging the sub-refrigerant to the ejector;
A first flow path switching device provided so that the refrigerant discharged from the ejector passes through at least one of the first evaporator and the second evaporator;
A second flow path switching device disposed upstream of the expansion device and provided to pass through the first expansion device or through the first expansion device and the second expansion device;
A total cooling mode in which a refrigerant flows through the first evaporator, the second evaporator, the third evaporator, and the first expansion device to cool the first cooling chamber and the second cooling chamber; And
And a refrigeration cooling mode in which refrigerant flows through the second evaporator, the third evaporator, the first expansion device, and the second expansion device to cool the second cooling chamber to a temperature lower than that of the total cooling mode. Refrigeration cycle. delete The method of claim 23,
The first flow path switching device,
A refrigeration cycle, characterized in that the refrigerant discharged from the ejector flows through the first evaporator and the second evaporator selectively. The method of claim 23,
The ejector,
A refrigeration cycle, characterized in that the main refrigerant discharged from the condenser and the sub-refrigerant discharged from the sub-evaporator are mixed and boosted, and then introduced into the compressor. main body;
A first cooling chamber provided inside the main body, and a second cooling chamber formed at a lower temperature than the first cooling chamber;
And a refrigeration cycle having a first evaporator and a second evaporator provided in the first cooling chamber, and a third evaporator provided in the second cooling chamber, and cooling the first cooling chamber and the second cooling chamber, and ,
The refrigeration cycle,
A first refrigerant circuit configured to flow to the compressor through a condenser, an ejector, the first evaporator, and the second evaporator;
A second refrigerant circuit configured such that the refrigerant bypasses the first evaporator in the first refrigerant circuit;
A third refrigerant circuit branched at a branch point provided downstream of the condenser in the first refrigerant circuit or the second refrigerant circuit, and configured to join the ejector through an expansion device and the third evaporator; and
The expansion device,
Including; a first expansion device and a second expansion device arranged in series with the first expansion device,
The third refrigerant circuit,
A 3a refrigerant circuit provided to pass through the first expansion device provided upstream of the third evaporator;
And a 3b refrigerant circuit provided to pass through the first expansion device and the second expansion device, and
The refrigeration cycle,
A total cooling mode in which refrigerant flows through the first refrigerant circuit and the third refrigerant circuit;
And a refrigerant cooling mode in which the refrigerant flows through the second refrigerant circuit and the third refrigerant circuit. delete delete The method of claim 27,
The ejector,
Refrigerator, characterized in that disposed in the direction of gravity than the third evaporator.

Images